Planetary transmissions with clutched input and a stationary member

ABSTRACT

The family of transmissions has a plurality of members that can be utilized in powertrains to provide at least seven forward speed ratios and one reverse speed ratio. The transmission family members include three planetary gear sets having six torque-transmitting mechanisms and two fixed interconnections. Also, one planetary gear member is continuously connected with the transmission housing. The powertrain includes an engine and torque converter that is not continuously connected to one of the planetary gear members and an output member that is continuously connected with at least one of the planetary gear members. The six torque-transmitting mechanisms provide interconnections between various gear members, the fixed interconnections, the input shaft, the output shaft, and the transmission housing, and are operated in combinations of three to establish at least seven forward speed ratios and at least one reverse speed ratio.

TECHNICAL FIELD

[0001] The present invention relates to a family of power transmissionshaving three planetary gear sets that are controlled by sixtorque-transmitting devices to provide at least seven forward speedratios and one reverse speed ratio.

BACKGROUND OF THE INVENTION

[0002] Passenger vehicles include a powertrain that is comprised of anengine, multi-speed transmission, and a differential or final drive. Themulti-speed transmission increases the overall operating range of thevehicle by permitting the engine to operate through its torque range anumber of times. The number of forward speed ratios that are availablein the transmission determines the number of times the engine torquerange is repeated. Early automatic transmissions had two speed ranges.This severely limited the overall speed range of the vehicle andtherefore required a relatively large engine that could produce a widespeed and torque range. This resulted in the engine operating at aspecific fuel consumption point during cruising, other than the mostefficient point. Therefore, manually-shifted (countershafttransmissions) were the most popular.

[0003] With the advent of three- and four-speed automatic transmissions,the automatic shifting (planetary gear) transmission increased inpopularity with the motoring public. These transmissions improved theoperating performance and fuel economy of the vehicle. The increasednumber of speed ratios reduces the step size between ratios andtherefore improves the shift quality of the transmission by making theratio interchanges substantially imperceptible to the operator undernormal vehicle acceleration.

[0004] It has been suggested that the number of forward speed ratios beincreased to six or more. Six-speed transmissions are disclosed in U.S.Pat. No. 4,070,927 issued to Polak on Jan. 31, 1978; U.S. Pat. No.6,071,208 issued to Koivunen on Jun. 6, 2000; U.S. Pat. No. 5,106,352issued to Lepelletier on Apr. 21, 1992; and U.S. Pat. No. 5,599,251issued to Beim and McCarrick on Feb. 4, 1997.

[0005] Six-speed transmissions offer several advantages over four- andfive-speed transmissions, including improved vehicle acceleration andimproved fuel economy. While many trucks employ power transmissionshaving six or more forward speed ratios, passenger cars are stillmanufactured with three- and four-speed automatic transmissions andrelatively few five or six-speed devices due to the size and complexityof these transmissions. The Polak transmission provides six forwardspeed ratios with three planetary gear sets, two clutches, and threebrakes. The Koivunen and Beim patents utilize six torque-transmittingdevices including four brakes and two clutches to establish six forwardspeed ratios and a reverse ratio. The Lepelletier patent employs threeplanetary gear sets, three clutches and two brakes to provide sixforward speeds. One of the planetary gear sets is positioned andoperated to establish two fixed speed input members for the remainingtwo planetary gear sets.

[0006] Seven-speed transmissions are disclosed in U.S. Pat. No.4,709,594 to Maeda; U.S. Pat. No. 6,053,839 to Baldwin et. al.; and U.S.Pat. No. 6,083,135 to Baldwin et. al. Seven- and eight-speedtransmissions provide further improvements in acceleration and fueleconomy over six-speed transmissions. However, like the six-speedtransmissions discussed above, the development of seven- and eight-speedtransmissions has been precluded because of complexity, size and cost.

SUMMARY OF THE INVENTION

[0007] It is an object of the present invention to provide an improvedfamily of transmissions having three planetary gear sets controlled toprovide at least seven forward speed ratios and one reverse speed ratio.

[0008] In one aspect of the present invention, the family oftransmissions has three planetary gear sets, each of which includes afirst, second and third member, which members may comprise a sun gear, aring gear, or a planet carrier assembly member.

[0009] In referring to the first, second and third gear sets in thisdescription and in the claims, these sets may be counted “first” to“third” in any order in the drawings (i.e., left to right, right toleft, etc.).

[0010] In another aspect of the present invention, each of the planetarygear sets may be of the single pinion-type or of the double pinion-type.

[0011] In yet another aspect of the present invention, the first memberof the first planetary gear set is continuously interconnected to thefirst member of the second planetary gear set through a firstinterconnecting member.

[0012] In yet another aspect of the present invention, the second memberof the second planetary gear set is continuously interconnected with thefirst member of the third planetary gear set through a secondinterconnecting member.

[0013] In yet another aspect of the invention, a third member of thesecond planetary gear set is continuously connected with a stationarymember (transmission housing).

[0014] In yet a further aspect of the invention, each family memberincorporates an input shaft which is not continuously connected with anymember of the planetary gear sets and an output shaft which iscontinuously connected with a member of the planetary gear sets.

[0015] In still a further aspect of the invention, a firsttorque-transmitting mechanism, such as a clutch, selectivelyinterconnects a member of the first, second or third planetary gear setwith the input shaft.

[0016] In another aspect of the invention, a second torque-transmittingmechanism, such as a clutch, selectively interconnects a member of thefirst, second or third planetary gear set or the first or secondinterconnecting member with the input shaft.

[0017] In a still further aspect of the invention, a thirdtorque-transmitting mechanism, such as a clutch, selectivelyinterconnects a member of the first, second or third planetary gear setwith the input shaft, the output shaft, or another member of the first,second or third planetary gear set.

[0018] In a still further aspect of the invention, a fourthtorque-transmitting mechanism, such as a clutch, selectivelyinterconnects a member of the first or third planetary gear set withanother member of the first, second or third planetary gear set.

[0019] In a still further aspect of the invention, a fifthtorque-transmitting mechanism, such as a clutch, selectivelyinterconnects a member of the first, second or third planetary gear setwith another member of the first, second or third planetary gear set.Alternatively, the fifth torque-transmitting mechanism, such as a brake,selectively connects a member of the first, second or third planetarygear set with the stationary member (transmission case).

[0020] In still another aspect of the invention, a sixthtorque-transmitting mechanism, such as a clutch, selectivelyinterconnects a member of the first or third planetary gear set withanother member of the first, second or third planetary gear set.Alternatively, the sixth torque-transmitting mechanism, such as a brake,selectively connects a member of the first or third planetary gear setwith the stationary member (transmission case).

[0021] In still another aspect of the invention, the sixtorque-transmitting mechanisms are selectively engageable incombinations of three to yield at least seven forward speed ratios andone reverse speed ratio.

[0022] The above object and other objects, features, and advantages ofthe present invention are readily apparent from the following detaileddescription of the best modes for carrying out the invention when takenin connection with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

[0023]FIG. 1a is a schematic representation of a powertrain including aplanetary transmission incorporating a family member of the presentinvention;

[0024]FIG. 1b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 1a;

[0025]FIG. 2a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0026]FIG. 2b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 2a;

[0027]FIG. 3a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0028]FIG. 3b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 3a;

[0029]FIG. 4a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0030]FIG. 4b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 4a;

[0031]FIG. 5a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0032]FIG. 5b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 5a;

[0033]FIG. 6a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0034]FIG. 6b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 6a;

[0035]FIG. 7a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0036]FIG. 7b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 7a;

[0037]FIG. 8a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0038]FIG. 8b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 8a;

[0039]FIG. 9a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0040]FIG. 9b is a truth table and chart depicting some of the operatingcharacteristics of the powertrain shown in FIG. 9a;

[0041]FIG. 10a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0042]FIG. 10b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 10a;

[0043]FIG. 11a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0044]FIG. 11b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 11a;

[0045]FIG. 12a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0046]FIG. 12b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 12a;

[0047]FIG. 13a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0048]FIG. 13b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 13a;

[0049]FIG. 14a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0050]FIG. 14b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 14a;

[0051]FIG. 15a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0052]FIG. 15b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 15a;

[0053]FIG. 16a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0054]FIG. 16b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 16a;

[0055]FIG. 17a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0056]FIG. 17b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 17a;

[0057]FIG. 18a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0058]FIG. 18b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 18a;

[0059]FIG. 19a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0060]FIG. 19b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 19a;

[0061]FIG. 20a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0062]FIG. 20b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 20a;

[0063]FIG. 21a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0064]FIG. 21b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 21a;

[0065]FIG. 22a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0066]FIG. 22b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 22a;

[0067]FIG. 23a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention;

[0068]FIG. 23b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 23a;

[0069]FIG. 24a is a schematic representation of a powertrain having aplanetary transmission incorporating another family member of thepresent invention; and

[0070]FIG. 24b is a truth table and chart depicting some of theoperating characteristics of the powertrain shown in FIG. 24a.

DESCRIPTION OF THE PREFERRED EMBODIMENT

[0071] Referring to the drawings, wherein like characters represent thesame or corresponding parts throughout the several views, there is shownin FIG. 1a a powertrain 10 having a conventional engine and torqueconverter 12, a planetary transmission 14, and a conventional finaldrive mechanism 16.

[0072] The planetary transmission 14 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 18, and an output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 18 includes three planetary gear sets 20, 30 and 40.

[0073] The planetary gear set 20 includes a sun gear member 22, a ringgear member 24, and a planet carrier assembly 26. The planet carrierassembly 26 includes a plurality of pinion gears 27 rotatably mounted ona carrier member 29 and disposed in meshing relationship with both thesun gear member 22 and the ring gear member 24.

[0074] The planetary gear set 30 includes a sun gear member 32, a ringgear member 34, and a planet carrier assembly member 36. The planetcarrier assembly member 36 includes a plurality of pinion gears 37rotatably mounted on a carrier member 39 and disposed in meshingrelationship with both the sun gear member 32 and the ring gear member34.

[0075] The planetary gear set 40 includes a sun gear member 42, a ringgear member 44, and a planet carrier assembly member 46. The planetcarrier assembly member 46 includes a plurality of pinion gears 47rotatably mounted on a carrier member 49 and disposed in meshingrelationship with both the sun gear member 42 and the ring gear member44.

[0076] The planetary gear arrangement also includes sixtorque-transmitting mechanisms 50, 52, 54, 56, 58 and 59. Thetorque-transmitting mechanisms 50, 52, 54 and 56 are rotating-typetorque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 58 and 59 are stationary-type torquetransmitting mechanisms, commonly termed brakes or reaction clutches.

[0077] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the ring gear member 24. The sun gear member 22 is continuouslyconnected with the ring gear member 44 through the interconnectingmember 70. The ring gear member 34 is continuously connected with theplanet carrier assembly member 46 through the interconnecting member 72.The sun gear member 42 is continuously connected with the transmissionhousing 60.

[0078] The planet carrier assembly member 26 is selectively connectablewith the input shaft 17 through the clutch 50. The sun gear member 32 isselectively connectable with the input shaft 17 through the clutch 52.The sun gear member 22 is selectively connectable with the planetcarrier assembly member 36 through the clutch 54. The planet carrierassembly member 26 is selectively connectable with the planet carrierassembly member 36 through the clutch 56. The ring gear member 44 isselectively connectable with the transmission housing 60 through thebrake 58. The planet carrier assembly member 26 is selectivelyconnectable with the transmission housing 60 through the brake 59.

[0079] As shown in FIG. 1b, and in particular the truth table disclosedtherein, the torque-transmitting mechanisms are selectively engaged incombinations of three to provide seven forward speed ratios and areverse speed ratio.

[0080] The reverse speed ratio is established with the engagement of theclutches 52, 54 and the brake 59. The clutch 52 connects the sun gearmember 32 to the input shaft 17. The clutch 54 connects the sun gearmember 22 to the planet carrier assembly member 36. The brake 59connects the planet carrier assembly member 36 to the transmissionhousing 60. The sun gear member 22 and the planet carrier assemblymember 36 rotate at the same speed as the ring gear member 44. Theplanet carrier assembly member 26 does not rotate. The ring gear member24 rotates at the same speed as the output shaft 19. The ring gearmember 24, and therefore the output shaft 19, rotates at a speeddetermined from the speed of the sun gear member 22 and the ringgear/sun gear tooth ratio of the planetary gear set 20. The ring gearmember 34 rotates at the same speed as the planet carrier assemblymember 46. The sun gear member 32 rotates at the same speed as the inputshaft 17. The planet carrier assembly member 36 rotates at a speeddetermined from the speed of the ring gear member 34, the speed of thesun gear member 32 and the ring gear/sun gear tooth ratio of theplanetary gear set 30. The sun gear member 42 does not rotate. Theplanet carrier assembly member 46 rotates at a speed determined from thespeed of the ring gear member 44 and the ring gear/sun gear tooth ratioof the planetary gear set 40. The numerical value of the reverse speedratio is determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 20, 30 and 40.

[0081] The first forward speed ratio is established with the engagementof the clutches 52, 56 and the brake 59. The clutch 52 connects the sungear member 32 to the input shaft 17. The clutch 56 connects the planetcarrier assembly member 26 to the planet carrier assembly member 36. Thebrake 59 connects the planet carrier assembly member 26 to thetransmission housing 60. The sun gear member 22 rotates at the samespeed as the ring gear member 44. The planet carrier assembly members26, 36 do not rotate. The ring gear member 24 rotates at the same speedas the output shaft 19. The ring gear member 24, and therefore theoutput shaft 19, rotates at a speed determined from the speed of the sungear member 22 and the ring gear/sun gear tooth ratio of the planetarygear set 20. The ring gear member 34 rotates at the same speed as theplanet carrier assembly member 46. The sun gear member 32 rotates at thesame speed as the input shaft 17. The ring gear member 34 rotates at aspeed determined from the speed of the sun gear member 32 and the ringgear/sun gear tooth ratio of the planetary gear set 30. The sun gearmember 42 does not rotate. The planet carrier assembly member 46 rotatesat a speed determined from the speed of the ring gear member 44 and thering gear/sun gear tooth ratio of the planetary gear set 40. Thenumerical value of the first forward speed ratio is determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 20, 30and 40.

[0082] The second forward speed ratio is established with the engagementof the clutches 52, 56 and the brake 58. The clutch 52 connects the sungear member 32 to the input shaft 17. The clutch 56 connects the planetcarrier assembly member 26 to the planet carrier assembly member 36. Thebrake 58 connects the ring gear member 44 to the transmission housing60. The sun gear member 22, the ring gear member 34 and the planetarygear set 40 do not rotate. The planet carrier assembly member 26 rotatesat the same speed as the planet carrier assembly member 36. The ringgear member 24 rotates at the same speed as the output shaft 19. Thering gear member 24, and therefore the output shaft 19, rotates at aspeed determined from the speed of the planet carrier assembly member 26and the ring gear/sun gear tooth ratio of the planetary gear set 20. Thesun gear member 32 rotates at the same speed as the input shaft 17. Theplanet carrier assembly member 36 rotates at a speed determined from thespeed of the sun gear member 32 and the ring gear/sun gear tooth ratioof the planetary gear set 30. The numerical value of the second forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 20, 30.

[0083] The third forward speed ratio is established with the engagementof the clutches 52, 54 and 56. The clutch 52 connects the sun gearmember 32 to the input shaft 17. The clutch 54 connects the sun gearmember 22 to the planet carrier assembly member 36. The clutch 56connects the planet carrier assembly member 26 to the planet carrierassembly member 36. The planetary gear set 20, the planet carrierassembly member 36 and the ring gear member 44 rotate at the same speedas the output shaft 19. The ring gear member 34 rotates at the samespeed as the planet carrier assembly member 46. The sun gear member 32rotates at the same speed as the input shaft 17. The planet carrierassembly member 36, and therefore the output shaft 19, rotates at aspeed determined from the speed of the ring gear member 34, the speed ofthe sun gear member 32 and the ring gear/sun gear tooth ratio of theplanetary gear set 30. The sun gear member 42 does not rotate. Theplanet carrier assembly member 46 rotates at a speed determined from thespeed of the ring gear member 44 and the ring gear/sun gear tooth ratioof the planetary gear set 40. The numerical value of the third forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 30, 40.

[0084] The fourth forward speed ratio is established with the engagementof the clutches 50, 52 and 56. The clutch 50 connects the planet carrierassembly member 26 to the input shaft 17. The clutch 52 connects the sungear member 32 to the input shaft 17. The clutch 56 connects the planetcarrier assembly member 26 to the planet carrier assembly member 36. Thesun gear member 22 rotates at the same speed as the ring gear member 44.The planet carrier assembly member 26, the planetary gear set 30 and theplanet carrier assembly member 46 rotate at the same speed as the inputshaft 17. The ring gear member 24 rotates at the same speed as theoutput shaft 19. The ring gear member 24, and therefore the output shaft19, rotates at a speed determined from the speed of the planet carrierassembly member 26, the speed of the sun gear member 22 and the ringgear/sun gear tooth ratio of the planetary gear set 20. The sun gearmember 42 does not rotate. The ring gear member 44 rotates at a speeddetermined from the speed of the planet carrier assembly member 46 andthe ring gear/sun gear tooth ratio of the planetary gear set 40. Thenumerical value of the fourth forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets20, 40.

[0085] The fifth forward speed ratio is established with the engagementof the clutches 50, 54 and 56. In this configuration, the input shaft 17is directly connected to the output shaft 19. The numerical value of thefifth forward speed ratio is 1.

[0086] The sixth forward speed ratio is established with the engagementof the clutches 50, 52 and 54. The clutch 50 connects the planet carrierassembly member 26 to the input shaft 17. The clutch 52 connects the sungear member 32 to the input shaft 17. The clutch 54 connects the sungear member 22 to the planet carrier assembly member 36. The sun gearmember 22 and the planet carrier assembly member 36 rotate at the samespeed as the ring gear member 44. The planet carrier assembly member 26and the sun gear member 32 rotate at the same speed as the input shaft17. The ring gear member 24 rotates at the same speed as the outputshaft 19. The ring gear member 24, and therefore the output shaft 19,rotates at a speed determined from the speed of the planet carrierassembly member 26, the speed of the sun gear member 22 and the ringgear/sun gear tooth ratio of the planetary gear set 20. The ring gearmember 34 rotates at the same speed as the planet carrier assemblymember 46. The planet carrier assembly member 36 rotates at a speeddetermined from the speed of the ring gear member 34, the speed of thesun gear member 32 and the ring gear/sun gear tooth ratio of theplanetary gear set 30. The sun gear member 42 does not rotate. Theplanet carrier assembly member 46 rotates at a speed determined from thespeed of the ring gear member 44 and the ring gear/sun gear tooth ratioof the planetary gear set 40. The numerical value of the sixth forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 20, 30 and 40.

[0087] The seventh forward speed ratio is established with theengagement of the clutches 50, 54 and the brake 58. The clutch 50connects the planet carrier assembly member 26 to the input shaft 17.The clutch 54 connects the sun gear member 22 to the planet carrierassembly member 36. The brake 58 connects the ring gear member 44 to thetransmission housing 60. The sun gear member 22, the planetary gear sets30, 40 do not rotate. The planet carrier assembly member 26 rotates atthe same speed as the input shaft 17. The ring gear member 24 rotates atthe same speed as the output shaft 19. The ring gear member 24, andtherefore the output shaft 19, rotates at a speed determined from thespeed of the planet carrier assembly member 26 and the ring gear/sungear tooth ratio of the planetary gear set 20. The numerical value ofthe seventh forward speed ratio is determined utilizing the ringgear/sun gear tooth ratio of the planetary gear set 20.

[0088] As set forth above, the engagement schedule for thetorque-transmitting mechanisms is shown in the truth table of FIG. 1b.This truth table also provides an example of speed ratios that areavailable utilizing the ring gear/sun gear tooth ratios given by way ofexample in FIG. 1b. The R1/S1 value is the tooth ratio of the planetarygear set 20; the R2/S2 value is the tooth ratio of the planetary gearset 30; and the R3/S3 value is the tooth ratio of the planetary gear set40. Also, the chart of FIG. 1b describes the ratio steps that areattained utilizing the sample of tooth ratios given. For example, thestep ratio between the first and second forward speed ratios is 1.62,while the step ratio between the reverse and first forward ratio is−0.93. It can also be readily determined from the truth table of FIG. 1bthat all of the single step forward ratio interchanges are of the singletransition variety, as are the double step forward ratio interchanges.

[0089]FIG. 2a shows a powertrain 110 having a conventional engine andtorque converter 12, a planetary transmission 114, and a conventionalfinal drive mechanism 16.

[0090] The planetary transmission 114 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 118, and an output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 118 includes three planetary gear sets 120, 130 and 140.

[0091] The planetary gear set 120 includes a sun gear member 122, a ringgear member 124, and a planet carrier assembly 126. The planet carrierassembly 126 includes a plurality of pinion gears 127 rotatably mountedon a carrier member 129 and disposed in meshing relationship with boththe sun gear member 122 and the ring gear member 124.

[0092] The planetary gear set 130 includes a sun gear member 132, a ringgear member 134, and a planet carrier assembly member 136. The planetcarrier assembly member 136 includes a plurality of pinion gears 137rotatably mounted on a carrier member 139 and disposed in meshingrelationship with both the sun gear member 132 and the ring gear member134.

[0093] The planetary gear set 140 includes a sun gear member 142, a ringgear member 144, and a planet carrier assembly member 146. The planetcarrier assembly member 146 includes a plurality of pinion gears 147rotatably mounted on a carrier member 149 and disposed in meshingrelationship with both the sun gear member 142 and the ring gear member144.

[0094] The planetary gear arrangement 118 also includes sixtorque-transmitting mechanisms 150, 152, 154, 156, 158 and 159. Thetorque-transmitting mechanisms 150, 152, 154, 156 and 158 arerotating-type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanism 159 is a stationary-type torquetransmitting mechanism, commonly termed brake or reaction clutch.

[0095] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 126. The ring gear member 124 iscontinuously connected with the planet carrier assembly member 136through the interconnecting member 170. The sun gear member 132 iscontinuously connected with the sun gear member 142 through theinterconnecting member 172. The ring gear member 134 is continuouslyconnected with the transmission housing 160.

[0096] The planet carrier assembly member 136 is selectively connectablewith the input shaft 17 through the clutch 150. The ring gear member 144is selectively connectable with the input shaft 17 through the clutch152. The planet carrier assembly member 146 is selectively connectablewith the input shaft 17 through the clutch 154. The ring gear member 144is selectively connectable with the planet carrier assembly member 126through the clutch 156. The planet carrier assembly member 146 isselectively connectable with the sun gear member 122 through the clutch158. The ring gear member 124 is selectively connectable with thetransmission housing 160 through the brake 159.

[0097] The truth table of FIG. 2b describes the engagement sequenceutilized to provide seven forward speed ratios and a reverse speed ratioin the planetary gear arrangement 118 shown in FIG. 2a.

[0098] The reverse speed ratio is established with the engagement of theclutches 150, 154 and 156. The clutch 150 connects the planet carrierassembly member 136 to the input shaft 17. The clutch 154 connects theplanet carrier assembly member 146 to the input shaft 17. The clutch 156connects the ring gear member 144 to the planet carrier assembly member126. The planet carrier assembly member 126 and the ring gear member 144rotate at the same speed as the output shaft 19. The planet carrierassembly members 136, 146 and the ring gear member 124 rotate at thesame speed as the input shaft 17. The ring gear member 134 does notrotate. The sun gear member 132 rotates at the same speed as the sungear member 142. The sun gear member 132 rotates at a speed determinedfrom the speed of the planet carrier assembly member 136 and the ringgear/sun gear tooth ratio of the planetary gear set 30. The ring gearmember 144, and therefore the output shaft 19 rotates at a speeddetermined from the speed of the planet carrier assembly member 146, thespeed of the sun gear member 142 and the ring gear/sun gear tooth ratioof the planetary gear set 140. The numerical value of the reverse speedratio is determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 130 and 140.

[0099] The first forward speed ratio is established with the engagementof the clutches 152, 158 and the brake 159. The clutch 152 connects theinput shaft 17 to the ring gear member 144. The clutch 158 connects thesun gear member 122 to the planet carrier assembly member 146. The brake159 connects the ring gear member 124 to the transmission housing 160.The sun gear member 122 rotates at the same speed as the planet carrierassembly member 146. The planet carrier assembly member 126 rotates atthe same speed as the output shaft 19. The ring gear member 124, theplanetary gear set 130 and the sun gear member 142 do not rotate. Theplanet carrier assembly member 126, and therefore the output shaft 19,rotates at a speed determined from the speed of the sun gear member 122and the ring gear/sun gear tooth ratio of the planetary gear set 120.The ring gear member 144 rotates at the same speed as the input shaft17. The planet carrier assembly member 146 rotates at a speed determinedfrom the speed of the ring gear member 144 and the ring gear/sun geartooth ratio of the planetary gear set 140. The numerical value of thefirst forward speed ratio is determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 120 and 140.

[0100] The second forward speed ratio is established with the engagementof the clutches 154, 158 and the brake 159. The clutch 154 connects theplanet carrier assembly member 146 to the input shaft 17. The clutch 158connects the sun gear member 122 to the planet carrier assembly member146. The brake 159 connects the ring gear member 124 to the transmissionhousing 160. The sun gear member 122 and the planet carrier assemblymember 146 rotate at the same speed as the input shaft 17. The planetcarrier assembly member 126 rotates at the same speed as the outputshaft 19. The ring gear member 124, the planetary gear set 130, and thesun gear member 142 do not rotate. The planet carrier assembly member126, and therefore the output shaft 19, rotates at a speed determinedfrom the speed of the sun gear member 122 and the ring gear/sun geartooth ratio of the planetary gear set 120. The numerical value of thesecond forward speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 120.

[0101] The third forward speed ratio is established with the engagementof the clutches 152, 154 and 158. The clutch 152 connects the ring gearmember 144 to the input shaft 17. The clutch 154 connects the planetcarrier assembly member 146 to the input shaft 17. The clutch 158connects the planet carrier assembly member 146 to the sun gear member122. The sun gear members 122, 132 and the planetary gear set 140 rotateat the same speed as the input shaft 17. The planet carrier assemblymember 126 rotates at the same speed as the output shaft 19. The ringgear member 124 rotates at the same speed as the planet carrier assemblymember 136. The planet carrier assembly member 126, and therefore theoutput shaft 19, rotates at a speed determined from the speed of thering gear member 124, the speed of the sun gear member 122 and the ringgear/sun gear tooth ratio of the planetary gear set 120. The ring gearmember 134 does not rotate. The planet carrier assembly member 136rotates at a speed determined from the speed of the sun gear member 132and the ring gear/sun gear tooth ratio of the planetary gear set 130.The numerical value of the third forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets120, 130.

[0102] The fourth forward speed ratio is established with the engagementof the clutches 154, 156 and 158. The clutch 154 connects the planetcarrier assembly member 146 to the input shaft 17. The clutch 156connects the ring gear member 144 to the planet carrier assembly member126. The clutch 158 connects the planet carrier assembly member 146 tothe sun gear member 122. The sun gear member 122 and the planet carrierassembly member 146 rotate at the same speed as the input shaft 17. Theplanet carrier assembly member 126 and the ring gear member 144 rotateat the same speed as the output shaft 19. The ring gear member 124rotates at the same speed as the planet carrier assembly member 136. Theplanet carrier assembly member 126, and therefore the output shaft 19,rotates at a speed determined from the speed of the ring gear member124, the speed of the sun gear member 122 and the ring gear/sun geartooth ratio of the planetary gear set 120. The ring gear member 134 doesnot rotate. The sun gear member 132 rotates at the same speed as the sungear member 142. The planet carrier assembly member 136 rotates at aspeed determined from the speed of the sun gear member 132 and the ringgear/sun gear tooth ratio of the planetary gear set 130. The ring gearmember 144 rotates at a speed determined from the speed of the planetcarrier assembly member 146, the speed of the sun gear member 142 andthe ring gear/sun gear tooth ratio of the planetary gear set 140. Thenumerical value of the fourth forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets120, 130 and 140.

[0103] The fifth forward speed ratio is established with the engagementof the clutches 152, 156 and 158. In this configuration, the input shaft17 is directly connected to the output shaft 19. The numerical value ofthe fifth forward speed ratio is 1.

[0104] The sixth forward speed ratio is established with the engagementof the clutches 150, 152 and 158. The clutch 150 connects the planetcarrier assembly member 136 to the input shaft 17. The clutch 152connects the ring gear member 144 to the input shaft 17. The clutch 158connects the sun gear member 122 to the planet carrier assembly member146. The sun gear member 122 rotates at the same speed as the planetcarrier assembly member 146. The planet carrier assembly member 126rotates at the same speed as the output shaft 19. The ring gear members124, 144 and the planet carrier assembly member 136 rotate at the samespeed as the input shaft 17. The planet carrier assembly member 126, andtherefore the output shaft 19, rotates at a speed determined from thespeed of the ring gear member 124, the speed of the sun gear member 122and the ring gear/sun gear tooth ratio of the planetary gear set 120.The ring gear member 134 does not rotate. The sun gear member 132rotates at the same speed as the sun gear member 142. The sun gearmember 132 rotates at a speed determined from the speed of the planetcarrier assembly member 136 and the ring gear/sun gear tooth ratio ofthe planetary gear set 130. The planet carrier assembly member 146rotates at a speed determined from the speed of the ring gear member144, the speed of the sun gear member 142 and the ring gear/sun geartooth ratio of the planetary gear set 140. The numerical value of thesixth forward speed ratio is determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 120, 130 and 140.

[0105] The seventh forward speed ratio is established with theengagement of the clutches 150, 156 and 158. The clutch 150 connects theplanet carrier assembly member 136 to the input shaft 17. The clutch 156connects the ring gear member 144 to the planet carrier assembly member126. The clutch 158 connects the sun gear member 122 to the planetcarrier assembly member 146. The sun gear member 122 rotates at the samespeed as the planet carrier assembly member 146. The planet carrierassembly member 126 and the ring gear member 144 rotate at the samespeed as the output shaft 19. The ring gear member 124 and the planetcarrier assembly member 136 rotate at the same speed as the input shaft17. The planet carrier assembly member 126, and therefore the outputshaft 19, rotates at a speed determined from the speed of the ring gearmember 124, the speed of the sun gear member 122 and the ring gear/sungear tooth ratio of the planetary gear set 120. The ring gear member 134does not rotate. The sun gear member 132 rotates at the same speed asthe sun gear member 142. The sun gear member 132 rotates at a speeddetermined from the speed of the planet carrier assembly member 136 andthe ring gear/sun gear tooth ratio of the planetary gear set 130. Theplanet carrier assembly member 146 rotates at a speed determined fromthe speed of the ring gear member 144, the speed of the sun gear member142 and the ring gear/sun gear tooth ratio of the planetary gear set140. The numerical value of the seventh forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 120, 130 and 140.

[0106] As set forth above, the truth table of FIG. 2b describes theengagement sequence of the torque-transmitting mechanisms utilized toprovide a reverse drive ratio and seven forward speed ratios. The truthtable also provides an example of the ratios that can be attained withthe family members shown in FIG. 2a utilizing the sample tooth ratiosgiven in FIG. 2b. The R1/S1 value is the tooth ratio of the planetarygear set 120; the R2/S2 value is the tooth ratio of the planetary gearset 130; and the R3/S3 value is the tooth ratio of the planetary gearset 140. Also shown in FIG. 2b are the ratio steps between single stepratios in the forward direction as well as the reverse to first ratiostep ratio. For example, the first to second step ratio is 1.47.

[0107] Turning to FIG. 3a, a powertrain 210 includes the engine andtorque converter 12, a planetary transmission 214, and a final drivemechanism 16. The planetary transmission 214 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 218, and an output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 218 includes three planetary gear sets 220, 230 and 240.

[0108] The planetary gear set 220 includes a sun gear member 222, a ringgear member 224, and a planet carrier assembly 226. The planet carrierassembly 226 includes a plurality of pinion gears 227 rotatably mountedon a carrier member 229 and disposed in meshing relationship with boththe sun gear member 222 and the ring gear member 224.

[0109] The planetary gear set 230 includes a sun gear member 232, a ringgear member 234, and a planet carrier assembly member 236. The planetcarrier assembly member 236 includes a plurality of pinion gears 237rotatably mounted on a carrier member 239 and disposed in meshingrelationship with both the sun gear member 232 and the ring gear member234.

[0110] The planetary gear set 240 includes a sun gear member 242, a ringgear member 244, and a planet carrier assembly member 246. The planetcarrier assembly member 246 includes a plurality of pinion gears 247rotatably mounted on a carrier member 249 and disposed in meshingrelationship with both the sun gear member 242 and the ring gear member244.

[0111] The planetary gear arrangement 218 also includes sixtorque-transmitting mechanisms 250, 252, 254, 256, 258 and 259 each ofwhich is a rotating type torque-transmitting mechanism, commonly termedclutch.

[0112] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the sun gear member 222. The planet carrier assembly member 226 iscontinuously connected with the planet carrier assembly member 246through the interconnecting member 270. The planet carrier assemblymember 236 is continuously connected with the ring gear member 244through the interconnecting member 272. The sun gear member 242 iscontinuously connected with the transmission housing 260.

[0113] The planet carrier assembly member 246 is selectively connectablewith the input shaft 17 through the clutch 250. The planet carrierassembly member 236 is selectively connectable with the input shaft 17through the clutch 252. The sun gear member 232 is selectivelyconnectable with the input shaft 17 through the clutch 254. The ringgear member 224 is selectively connectable with the ring gear member 234through the clutch 256. The sun gear member 222 is selectivelyconnectable with the sun gear member 232 through the clutch 258. The sungear member 222 is selectively connectable with the ring gear member 234through the clutch 259.

[0114] As shown in the truth table in FIG. 3b, the torque-transmittingmechanisms are engaged in combinations of three to establish sevenforward speed ratios and one reverse ratio.

[0115] The reverse speed ratio is established with the engagement of theclutches 252, 256 and 258. The clutch 252 connects the planet carrierassembly member 236 to the input shaft 17. The clutch 256 connects thering gear member 224 to the ring gear member 234. The clutch 258connects the sun gear member 222 to the sun gear member 232. The sungear members 222, 232 rotate at the same speed as the output shaft 19.The planet carrier assembly member 226 rotates at the same speed as theplanet carrier assembly member 246. The ring gear member 224 rotates atthe same speed as the ring gear member 234. The sun gear member 222, andtherefore the output shaft 19, rotates at a speed determined from thespeed of the ring gear member 224, the speed of the planet carrierassembly member 226 and the ring gear/sun gear tooth ratio of theplanetary gear set 220. The planet carrier assembly member 236 and thering gear member 244 rotate at the same speed as the input shaft 17. Thesun gear member 232 rotates at a speed determined from the speed of thering gear member 234, the speed of the planet carrier assembly member236 and the ring gear/sun gear tooth ratio of the planetary gear set230. The sun gear member 242 does not rotate. The planet carrierassembly member 246 rotates at a speed determined from the speed of thering gear member 244 and the ring gear/sun gear tooth ratio of theplanetary gear set 240. The numerical value of the reverse speed ratiois determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 220, 230 and 240.

[0116] The first forward speed ratio is established with the engagementof the clutches 250, 254 and 256. The clutch 250 connects the planetcarrier assembly member 246 to the input shaft 17. The clutch 254connects the sun gear member 232 to the input shaft 17. The clutch 256connects the ring gear member 224 to the ring gear member 234. The sungear member 222 rotates at the same speed as the output shaft 19. Theplanet carrier assembly members 226, 246 and the sun gear member 232rotate at the same speed as the input shaft 17. The ring gear member 224rotates at the same speed as the ring gear member 234. The sun gearmember 222, and therefore the output shaft 19, rotates at a speeddetermined from the speed of the ring gear member 224, the speed of theplanet carrier assembly member 226 and the ring gear/sun gear toothratio of the planetary gear set 220. The planet carrier assembly member236 rotates at the same speed as the ring gear member 244. The planetcarrier assembly member 236 rotates at a speed determined from the speedof the ring gear member 234, the speed of the sun gear member 232 andthe ring gear/sun gear tooth ratio of the planetary gear set 230. Thesun gear member 242 does not rotate. The ring gear member 244 rotates ata speed determined from the speed of the planet carrier assembly member246 and the ring gear/sun gear tooth ratio of the planetary gear set240. The numerical value of the first forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets220, 230 and 240.

[0117] The second forward speed ratio is established with the engagementof the clutches 252, 254 and 256. The clutch 252 connects the planetcarrier assembly member 236 to the input shaft 17. The clutch 254connects the sun gear member 232 to the input shaft 17. The clutch 256connects the ring gear member 224 to the ring gear member 234. The sungear member 222 rotates at the same speed as the output shaft 19. Theplanet carrier assembly member 226 rotates at the same speed as theplanet carrier assembly member 246. The ring gear members 224, 234 andthe planetary gear set 230 rotate at the same speed as the input shaft17. The sun gear member 222, and therefore the output shaft 19, rotatesat a speed determined from the speed of the ring gear member 224, thespeed of the planet carrier assembly member 226 and the ring gear/sungear tooth ratio of the planetary gear set 220. The sun gear member 242does not rotate. The planet carrier assembly member 246 rotates at aspeed determined from the speed of the ring gear member 244 and the ringgear/sun gear tooth ratio of the planetary gear set 240. The numericalvalue of the second forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 220 and 240.

[0118] The third forward speed ratio is established with the engagementof the clutches 254, 256 and 259. The clutch 254 connects the sun gearmember 232 to the input shaft 17. The clutch 256 connects the ring gearmember 224 to the ring gear member 234. The clutch 256 connects the sungear member 222 to the ring gear member 234. The planetary gear set 220,the ring gear member 234 and the planet carrier assembly member 246rotate at the same speed as the output shaft 19. The planet carrierassembly member 236 rotates at the same speed as the ring gear member244. The sun gear member 232 rotates at the same speed as the inputshaft 17. The ring gear member 234, and therefore the output shaft 19,rotates at a speed determined from the speed of the planet carrierassembly member 236, the speed of the sun gear member 232 and the ringgear/sun gear tooth ratio of the planetary gear set 230. The sun gearmember 242 does not rotate. The planet carrier assembly member 246rotates at a speed determined from the speed of the ring gear member 244and the ring gear/sun gear tooth ratio of the planetary gear set 240.The numerical value of the third forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets230 and 240.

[0119] The fourth forward speed ratio is established with the engagementof the clutches 252, 256 and 259. The clutch 252 connects the planetcarrier assembly member 236 to the input shaft 17. The clutch 256connects ring gear member 224 to the ring gear member 234. The clutch259 connects the sun gear member 222 to the ring gear member 234. Theplanetary gear set 220, the ring gear member 234 and the planet carrierassembly member 246 rotates at the same speed as the output shaft 19.The planet carrier assembly member 236 and the ring gear member 244rotate at the same speed as the input shaft 17. The sun gear member 242does not rotate. The planet carrier assembly member 246, and thereforethe output shaft 19, rotates at a speed determined from the speed of thering gear member 244 and the ring gear/sun gear tooth ratio of theplanetary gear set 240. The numerical value of the fourth forward speedratio is determined utilizing the ring gear/sun gear tooth ratio of theplanetary gear set 240.

[0120] The fifth forward speed ratio is established with the engagementof the clutches 252, 258 and 259. In this configuration, the input shaft17 is directly connected to the output shaft 19. The numerical value ofthe fifth forward speed ratio is 1.

[0121] The sixth forward speed ratio is established with the engagementof the clutches 250, 258 and 259. The clutch 250 connects planet carrierassembly member 246 to the input shaft 17. The clutch 258 connects thesun gear member 222 to the sun gear member 232. The clutch 259 connectsthe sun gear member 222 to the ring gear member 234. The sun gear member222, the planetary gear set 230 and the ring gear member 244 rotate atthe same speed as the output shaft 19. The planet carrier assemblymembers 226, 246 rotate at the same speed as the input shaft 17. The sungear member 242 does not rotate. The ring gear member 244, and thereforethe output shaft 19, rotates at a speed determined from the speed of theplanet carrier assembly member 246 and the ring gear/sun gear toothratio of the planetary gear set 240. The numerical value of the sixthforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 240.

[0122] The seventh forward speed ratio is established with theengagement of the clutches 250, 254 and 259. The clutch 250 connects theplanet carrier assembly member 246 to the input shaft 17. The clutch 254connects the sun gear member 232 to the input shaft 17. The clutch 259connects the sun gear member 222 to the ring gear member 234. The sungear member 222 and the ring gear member 234 rotate at the same speed asthe output shaft 19. The planet carrier assembly members 226, 246 andthe sun gear member 232 rotate at the same speed as the input shaft 17.The planet carrier assembly member 236 rotates at the same speed as thering gear member 244. The ring gear member 234, and therefore the outputshaft 19, rotates at a speed determined from the speed of the planetcarrier assembly member 236, the speed of the sun gear member 232 andthe ring gear/sun gear tooth ratio of the planetary gear set 230. Thesun gear member 242 does not rotate. The ring gear member 244 rotates ata speed determined from the speed of the planet carrier assembly member246 and the ring gear/sun gear tooth ratio of the planetary gear set240. The numerical value of the seventh forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 230, 240.

[0123] As previously set forth, the truth table of FIG. 3b describes thecombinations of engagements utilized for the seven forward speed ratiosand reverse ratio. The truth table also provides an example of speedratios that are available with the family member described above. Theseexamples of speed ratios are determined utilizing the tooth ratios givenin FIG. 3b. The R1/S1 value is the tooth ratio of the planetary gear set220; the R2/S2 value is the tooth ratio of the planetary gear set 230;and the R3/S3 value is the tooth ratio of the planetary gear set 240.Also depicted in FIG. 3b is a chart representing the ratio steps betweenadjacent forward speed ratios and the reverse speed ratio. For example,the first to second ratio interchange has a step of 1.45. It can also bereadily determined from the truth table of FIG. 3b that all of thesingle step forward ratio interchanges are of the single transitionvariety, except for the reverse to first step ratio.

[0124] A powertrain 310, shown in FIG. 4a, includes the engine andtorque converter 12, a planetary transmission 314, and the final drivemechanism 16. The planetary transmission 314 includes an input shaft 17continuously connected with the engine and torque converter 12, aplanetary gear arrangement 318, and output shaft 19 continuouslyconnected with the final drive mechanism 16. The planetary geararrangement 318 includes three planetary gear sets 320, 330 and 340.

[0125] The planetary gear set 320 includes a sun gear member 322, a ringgear member 324, and a planet carrier assembly member 326. The planetcarrier assembly member 326 includes a plurality of pinion gears 327rotatably mounted on a carrier member 329 and disposed in meshingrelationship with both the sun gear member 322 and the ring gear member324.

[0126] The planetary gear set 330 includes a sun gear member 332, a ringgear member 334, and a planet carrier assembly member 336. The planetcarrier assembly member 336 includes a plurality of pinion gears 337rotatably mounted on a carrier member 339 and disposed in meshingrelationship with both the sun gear member 332 and the ring gear member334.

[0127] The planetary gear set 340 includes a sun gear member 342, a ringgear member 344, and a planet carrier assembly member 346. The planetcarrier assembly member 346 includes a plurality of pinion gears 347rotatably mounted on a carrier member 349 and disposed in meshingrelationship with both the sun gear member 342 and the ring gear member344.

[0128] The planetary gear arrangement 318 also includes sixtorque-transmitting mechanisms 350, 352, 354, 356, 358 and 359. Thetorque-transmitting mechanisms 350, 352, 354, 356 and 358 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanism 359 is a stationary-type torquetransmitting mechanism, commonly termed brake or reaction clutch.

[0129] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the ring gear member 344. The planet carrier assembly member 326 iscontinuously connected with the planet carrier assembly member 336through the interconnecting member 370. The ring gear member 334 iscontinuously connected with the planet carrier assembly member 346through the interconnecting member 372. The sun gear member 332 iscontinuously connected with the transmission housing 360.

[0130] The sun gear member 322 is selectively connectable with the inputshaft 17 through the clutch 350. The sun gear member 342 is selectivelyconnectable with the input shaft 17 through the clutch 352. The ringgear member 324 is selectively connectable with the planet carrierassembly member 326 through the clutch 354. The planet carrier assemblymember 336 is selectively connectable with the ring gear member 344through the clutch 356. The planet carrier assembly member 346 isselectively connectable with the sun gear member 342 through the clutch358. The ring gear member 324 is selectively connectable with thetransmission housing 360 through the brake 359.

[0131] The truth tables given in FIGS. 4b, 5 b, 6 b, 7 b, 8 b, 9 b, 10b, 11 b, 12 b, 13 b, 14 b, 15 b, 16 b, 17 b, 18 b, 19 b, 20 b, 21 b, 22b, 23 b and 24 b show the engagement sequences for thetorque-transmitting mechanisms to provide at least seven forward speedratios and at least one reverse ratio. As shown and described above forthe configuration in FIGS. 1a, 2 a and 3 a, those skilled in the artwill understand from the respective truth tables how the speed ratiosare established through the planetary gear sets identified in thewritten description.

[0132] The truth table shown in FIG. 4b describes the engagementcombination and the engagement sequence necessary to provide the reversedrive ratio and seven forward speed ratios. A sample of the numericalvalues for the ratios is also provided in the truth table of FIG. 4b.These values are determined utilizing the ring gear/sun gear toothratios also given in FIG. 4b. The R1/S1 value is the tooth ratio for theplanetary gear set 320; the R2/S2 value is the tooth ratio for theplanetary gear set 330; and the R3/S3 value is the tooth ratio for theplanetary gear set 340. Also given in FIG. 4b is a chart describing thestep ratios between the adjacent forward speed ratios and the reverse tofirst forward speed ratio. For example, the first to second forwardspeed ratio step is 1.40. It can be readily determined from the truthtable of FIG. 4b that each of the forward single step ratio interchangesis a single transition shift, as are the double step interchanges.

[0133] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 340. The numerical values ofthe first and seventh forward speed ratios are determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 330 and 340.The numerical value of the second forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratio of the planetary gear set320. The numerical value of the third forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets320, 330 and 340. The numerical value of the fourth forward speed ratiois determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 320 and 330. The numerical value of the fifthforward speed ratio is 1. The numerical value of the sixth forward speedratio is determined utilizing the ring gear/sun gear tooth ratio of theplanetary gear set 330.

[0134] A powertrain 410, shown in FIG. 5a, includes the engine andtorque converter 12, a planetary transmission 414 and the final drivemechanism 16. The planetary transmission 414 includes a planetary geararrangement 418, input shaft 17 and output shaft 19. The planetary geararrangement 418 includes three simple planetary gear sets 420, 430 and440.

[0135] The planetary gear set 420 includes a sun gear member 422, a ringgear member 424, and a planet carrier assembly 426. The planet carrierassembly 426 includes a plurality of pinion gears 427 rotatably mountedon a carrier member 429 and disposed in meshing relationship with boththe sun gear member 422 and the ring gear member 424.

[0136] The planetary gear set 430 includes a sun gear member 432, a ringgear member 434, and a planet carrier assembly member 436. The planetcarrier assembly member 436 includes a plurality of pinion gears 437rotatably mounted on a carrier member 439 and disposed in meshingrelationship with both the sun gear member 432 and the ring gear member434.

[0137] The planetary gear set 440 includes a sun gear member 442, a ringgear member 444, and a planet carrier assembly member 446. The planetcarrier assembly member 446 includes a plurality of pinion gears 447rotatably mounted on a carrier member 449 and disposed in meshingrelationship with both the sun gear member 442 and the ring gear member444.

[0138] The planetary gear arrangement 418 also includes sixtorque-transmitting mechanisms 450, 452, 454, 456, 458 and 459 each ofwhich is a rotating type torque-transmitting mechanism, commonly termedclutch.

[0139] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 446. The ring gear member 424 iscontinuously connected with the sun gear member 432 through theinterconnecting member 470. The planet carrier assembly member 436 iscontinuously connected with the ring gear member 444 through theinterconnecting member 472. The ring gear member 434 is continuouslyconnected with the transmission housing 460.

[0140] The sun gear member 422 is selectively connectable with the inputshaft 17 through the clutch 450. The sun gear member 442 is selectivelyconnectable with input shaft 17 through the clutch 452. The sun gearmember 432 is selectively connectable with the planet carrier assemblymember 446 through the clutch 454. The sun gear member 432 isselectively connectable with the sun gear member 442 through the clutch456. The sun gear member 422 is selectively connectable with the planetcarrier assembly member 436 through the clutch 458. The planet carrierassembly member 426 is selectively connectable with the planet carrierassembly member 436 through the clutch 459.

[0141] The truth table shown in FIG. 5b describes the engagementcombination and sequence of the torque-transmitting mechanisms 450, 452,454, 456, 458 and 459 that are employed to provide the reverse driveratio and the seven forward speed ratios. It should be noted that thetorque-transmitting mechanisms 450 and 459 are engaged through theneutral condition to simplify the forward/reverse interchange.

[0142] Also given in the truth table of FIG. 5b is a set of numericalvalues that are attainable with the present invention utilizing the ringgear/sun gear tooth ratios shown. The R1/S1 value is the tooth ratio ofthe planetary gear set 420; the R2/S2 value is the tooth ratio of theplanetary gear set 430; and the R3/S3 value is the tooth ratio of theplanetary gear set 440. As can also be determined from the truth tableof FIG. 5b, the single step forward interchanges are single transitionshifts.

[0143]FIG. 5b also provides a chart of the ratio steps between adjacentforward ratios and between the reverse and first forward ratio. Forexample, the ratio step between the first and second forward ratios is1.81. Those skilled in the art will recognize that the numerical valuesof the reverse and first forward speed ratios are determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 320, 330and 340. The numerical value of the second forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 340. The numerical values of the third, fourth and sixthforward speed ratios are determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 330 and 340. The numerical valueof the fifth forward speed ratio is 1. The numerical value of theseventh forward speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 330.

[0144] A powertrain 510, shown in FIG. 6a, includes an engine and torqueconverter 12, a planetary gear transmission 514 and the final drivemechanism 16. The planetary transmission 514 includes the input shaft17, a planetary gear arrangement 518 and the output shaft 19. Theplanetary gear arrangement 518 includes three planetary gear sets 520,530 and 540.

[0145] The planetary gear set 520 includes a sun gear member 522, a ringgear member 524, and a planet carrier assembly 526. The planet carrierassembly 526 includes a plurality of pinion gears 527 rotatably mountedon a carrier member 529 and disposed in meshing relationship with boththe sun gear member 522 and the ring gear member 524.

[0146] The planetary gear set 530 includes a sun gear member 532, a ringgear member 534, and a planet carrier assembly member 536. The planetcarrier assembly member 536 includes a plurality of pinion gears 537rotatably mounted on a carrier member 539 and disposed in meshingrelationship with both the sun gear member 532 and the ring gear member534.

[0147] The planetary gear set 540 includes a sun gear member 542, a ringgear member 544, and a planet carrier assembly member 546. The planetcarrier assembly member 546 includes a plurality of pinion gears 547rotatably mounted on a carrier member 549 and disposed in meshingrelationship with both the sun gear member 542 and the ring gear member544.

[0148] The planetary gear arrangement 518 also includes sixtorque-transmitting mechanisms 550, 552, 554, 556, 558 and 559. Thetorque-transmitting mechanisms 550, 552, 554 and 556 are rotating typetorque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 558 and 559 are stationary-type torquetransmitting mechanisms, commonly termed brakes or reaction clutches.

[0149] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the ring gear member 524. The sun gear member 522 is continuouslyconnected with the sun gear member 532 through the interconnectingmember 570. The ring gear member 524 is continuously connected with theplanet carrier assembly member 546 through the interconnecting member572. The planet carrier assembly member 526 is continuously connectedwith the transmission housing 560.

[0150] The ring gear member 534 is selectively connectable with theinput shaft 17 through the clutch 550. The sun gear member 542 isselectively connectable with the input shaft 17 through the clutch 552.The ring gear member 534 is selectively connectable with the ring gearmember 544 through the clutch 554. The planet carrier assembly member536 is selectively connectable with the ring gear member 544 through theclutch 556. The ring gear member 534 is selectively connectable with thetransmission housing 560 through the brake 558. The planet carrierassembly member 536 is selectively connectable with the transmissionhousing 560 through the brake 559.

[0151] The truth table shown in FIG. 6b describes the engagementsequence and combination of the torque-transmitting mechanisms toprovide the reverse speed ratios and seven forward speed ratios. Itshould be noted that the torque-transmitting mechanisms 554 and 556 canremain engaged through the neutral condition, thereby simplifying theforward/reverse interchange. It can also be determined from the truthtable of FIG. 6b that all of the single and double step forward ratiointerchanges are of the single transition variety. The chart of FIG. 6bdescribes the ratio steps between adjacent forward speed ratios and theratio step between the reverse and first forward speed ratio.

[0152] Those skilled in the art, upon reviewing the truth table and theschematic representation of FIG. 6a, can determine that the numericalvalue of the reverse speed ratio is determined utilizing the ringgear/sun gear tooth ratio of the planetary gear set 520. The numericalvalue of the first forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 520 and 540. Thenumerical values of the second, fourth and seventh forward speed ratiosare determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 520, 530 and 540. The numerical value of the thirdforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 540. The numerical value of the fifthforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 520 and 530. The numerical value ofthe sixth forward speed ratio is 1.

[0153] The sample speed ratios given in the truth table are determinedutilizing the tooth ratio values also given in FIG. 6b. The R1/S1 valueis the tooth ratio of the planetary gear set 520; the R2/S2 value is thetooth ratio of the planetary gear set 530; and the R3/S3 value is thetooth ratio of the planetary gear set 540.

[0154] A powertrain 610, shown in FIG. 7a, has the engine and torqueconverter 12, a planetary transmission 614 and the final drive mechanism16. The planetary transmission 614 includes the input shaft 17, aplanetary gear arrangement 618 and the output shaft 19. The planetarygear arrangement 618 includes three planetary gear sets 620, 630 and640.

[0155] The planetary gear set 620 includes a sun gear member 622, a ringgear member 624, and a planet carrier assembly 626. The planet carrierassembly 626 includes a plurality of pinion gears 627 rotatably mountedon a carrier member 629 and disposed in meshing relationship with boththe sun gear member 622 and the ring gear member 624.

[0156] The planetary gear set 630 includes a sun gear member 632, a ringgear member 634, and a planet carrier assembly member 636. The planetcarrier assembly member 636 includes a plurality of pinion gears 637rotatably mounted on a carrier member 639 and disposed in meshingrelationship with both the sun gear member 632 and the ring gear member634.

[0157] The planetary gear set 640 includes a sun gear member 642, a ringgear member 644, and a planet carrier assembly member 646. The planetcarrier assembly member 646 includes a plurality of pinion gears 647rotatably mounted on a carrier member 649 and disposed in meshingrelationship with both the sun gear member 642 and the ring gear member644.

[0158] The planetary gear arrangement 618 also includes sixtorque-transmitting mechanisms 650, 652, 654, 656, 658 and 659. Thetorque-transmitting mechanisms 650, 652, 654, 656 and 658 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanism 659 is a stationary-type torquetransmitting mechanism, commonly termed brake or reaction clutch.

[0159] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the ring gear member 634. The ring gear member 624 is continuouslyconnected with the planet carrier assembly member 646 through theinterconnecting member 670. The planet carrier assembly member 636 iscontinuously connected with the ring gear member 644 through theinterconnecting member 672. The sun gear member 642 is continuouslyconnected with the transmission housing 660.

[0160] The sun gear member 622 is selectively connectable with the inputshaft 17 through the clutch 650. The sun gear member 632 is selectivelyconnectable with the input shaft 17 through the clutch 652. The ringgear member 634 is selectively connectable with the planet carrierassembly member 646 through the clutch 654. The planet carrier assemblymember 626 is selectively connectable with the planet carrier assemblymember 636 through the clutch 656. The planet carrier assembly member626 is selectively connectable with the sun gear member 632 through theclutch 658. The planet carrier assembly member 646 is selectivelyconnectable with the transmission housing 660 through the brake 659.

[0161] The truth table shown in FIG. 7b describes the combination oftorque-transmitting mechanism engagements that will provide the reversedrive ratio and seven forward speed ratios, as well as the sequence ofthese engagements and interchanges. The torque-transmitting mechanisms650 and 658 can be engaged through the neutral condition, therebysimplifying the forward/reverse interchange.

[0162] The ratio values given are by way of example and are establishedutilizing the ring gear/sun gear tooth ratios given in FIG. 7b. Forexample, the R1/S1 value is the tooth ratio of the planetary gear set620; the R2/S2 value is the tooth ratio of the planetary gear set 630;and the R3/S3 value is the tooth ratio of the planetary gear set 640.The ratio steps between adjacent forward ratios and the reverse to firstratio are also given in FIG. 7b.

[0163] Those skilled in the art will, upon reviewing the truth table ofFIG. 7b, recognize that the numerical value of the reverse speed ratiois determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 620, 630. The numerical values of the first andfourth forward speed ratio are determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 620, 630 and 640. Thenumerical values of the second, third and seventh forward speed ratiosare determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 630, 640. The numerical value of the fifth forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 620, 640. The numerical value of sixthforward speed ratio is 1.

[0164] A powertrain 710, shown in FIG. 8a, has the conventional engineand torque converter 12, a planetary transmission 714, and theconventional final drive mechanism 16. The engine and torque converter12 are drivingly connected with the planetary transmission 714 throughthe input shaft 17. The planetary transmission 714 is drivinglyconnected with the final drive mechanism 16 through the output shaft 19.The planetary transmission 714 includes a planetary gear arrangement 718that has a first planetary gear set 720, a second planetary gear set730, and a third planetary gear set 740.

[0165] The planetary gear set 720 includes a sun gear member 722, a ringgear member 724, and a planet carrier assembly 726. The planet carrierassembly 726 includes a plurality of pinion gears 727 rotatably mountedon a carrier member 729 and disposed in meshing relationship with boththe sun gear member 722 and the ring gear member 724.

[0166] The planetary gear set 730 includes a sun gear member 732, a ringgear member 734, and a planet carrier assembly member 736. The planetcarrier assembly member 736 includes a plurality of pinion gears 737rotatably mounted on a carrier member 739 and disposed in meshingrelationship with both the sun gear member 732 and the ring gear member734.

[0167] The planetary gear set 740 includes a sun gear member 742, a ringgear member 744, and a planet carrier assembly member 746. The planetcarrier assembly member 746 includes a plurality of pinion gears 747rotatably mounted on a carrier member 749 and disposed in meshingrelationship with both the sun gear member 742 and the ring gear member744.

[0168] The planetary gear arrangement 718 also includes sixtorque-transmitting mechanisms 750, 752, 754, 756, 758 and 759. Thetorque-transmitting mechanisms 750, 752, 754 and 756 are rotating typetorque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 758 and 759 are stationary-type torquetransmitting mechanisms, commonly termed brakes or reaction clutches.

[0169] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the ring gear member 724. The sun gear member 722 is continuouslyconnected with the ring gear member 744 through the interconnectingmember 770. The ring gear member 734 is continuously connected with theplanet carrier assembly member 746 through the interconnecting member772. The sun gear member 742 is continuously connected with thetransmission housing 760.

[0170] The planet carrier assembly member 726 is selectively connectablewith the input shaft 17 through the clutch 750. The sun gear member 732is selectively connectable with the input shaft 17 through the clutch752. The sun gear member 722 is selectively connectable with the planetcarrier assembly member 736 through the clutch 754. The planet carrierassembly member 726 is selectively connectable with the planet carrierassembly member 736 through the clutch 756. The planet carrier assemblymember 726 is selectively connectable with the transmission housing 760through the brake 758. The planet carrier assembly member 736 isselectively connectable with the transmission housing 760 through thebrake 759.

[0171] The truth table of FIG. 8b defines the torque-transmittingmechanism engagement sequence utilized for each of the forward speedratios and the reverse speed ratio. Also given in the truth table is aset of numerical values that are attainable with the present inventionutilizing the ring gear/sun gear tooth ratios given in FIG. 8b. TheR1/S1 value is the tooth ratio of the planetary gear set 720; the R2/S2value is the tooth ratio of the planetary gear set 730; and the R3/S3value is the tooth ratio of the planetary gear set 740. As can also bedetermined from the truth table of FIG. 8b, the single step forwardinterchanges are single transition shifts, as are the double stepinterchanges in the forward direction.

[0172]FIG. 8b also provides a chart of the ratio steps between adjacentforward ratios and between the reverse and first forward ratio. Forexample, the ratio step between the first and second forward ratios is1.60. Those skilled in the art will recognize that the numerical valuesof the reverse, first, fifth and seventh forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 720, 730 and 740. The numerical value of the secondforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 730 and 740. The numerical value ofthe third forward speed ratio is determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 720 and 740. The numericalvalue of the fourth forward speed ratio is 1. The numerical value of thesixth forward speed ratio is determined utilizing the ring gear/sun geartooth ratio of the planetary gear set 720.

[0173] A powertrain 810, shown in FIG. 9a, has the conventional engineand torque converter 12, a planetary transmission 814, and the finaldrive mechanism 16. The engine and torque converter 12 are drivinglyconnected with the planetary transmission 814 through the input shaft17. The planetary transmission 814 is drivingly connected with the finaldrive mechanism 16 through the output shaft 19. The planetarytransmission 814 includes a planetary gear arrangement 818 that has afirst planetary gear set 820, a second planetary gear set 830, and athird planetary gear set 840.

[0174] The planetary gear set 820 includes a sun gear member 822, a ringgear member 824, and a planet carrier assembly 826. The planet carrierassembly 826 includes a plurality of pinion gears 827 rotatably mountedon a carrier member 829 and disposed in meshing relationship with boththe sun gear member 822 and the ring gear member 824.

[0175] The planetary gear set 830 includes a sun gear member 832, a ringgear member 834, and a planet carrier assembly member 836. The planetcarrier assembly member 836 includes a plurality of pinion gears 837rotatably mounted on a carrier member 839 and disposed in meshingrelationship with both the sun gear member 832 and the ring gear member834.

[0176] The planetary gear set 840 includes a sun gear member 842, a ringgear member 844, and a planet carrier assembly member 846. The planetcarrier assembly member 846 includes a plurality of pinion gears 847rotatably mounted on a carrier member 849 and disposed in meshingrelationship with both the sun gear member 842 and the ring gear member844.

[0177] The planetary gear arrangement 818 also includes sixtorque-transmitting mechanisms 850, 852, 854, 856, 858 and 859. Thetorque-transmitting mechanisms 850, 852, 854, 856 and 858 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanism 859 is a stationary-type torquetransmitting mechanism, commonly termed brake or reaction clutch.

[0178] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the ring gear member 824. The sun gear member 822 is continuouslyconnected with the ring gear member 834 through the interconnectingmember 870. The planet carrier assembly member 836 is continuouslyconnected with the ring gear member 844 through the interconnectingmember 872. The sun gear member 832 is continuously connected with thetransmission housing 860.

[0179] The sun gear member 822 is selectively connectable with the inputshaft 17 through the clutch 850. The planet carrier assembly member 826is selectively connectable with the input shaft 17 through the clutch852. The sun gear member 842 is selectively connectable with the inputshaft 17 through the clutch 854. The sun gear member 822 is selectivelyconnectable with the planet carrier assembly member 846 through theclutch 856. The ring gear member 824 is selectively connectable with theplanet carrier assembly member 836 through the clutch 858. The planetcarrier assembly member 846 is selectively connectable with thetransmission housing 860 through the brake 859.

[0180] The truth table shown in FIG. 9b defines the torque-transmittingmechanism engagement sequence that provides the reverse speed ratio andseven forward speed ratios shown in the truth table and available withthe planetary gear arrangement 818. The truth table indicates that thetorque-transmitting mechanisms 854 and 858 can remain engaged throughthe neutral condition, thereby simplifying the forward/reverseinterchange. A sample of numerical values for the individual ratios isalso given in the truth table of FIG. 9b. These numerical values havebeen calculated using the ring gear/sun gear tooth ratios also given byway of example in FIG. 9b. The R1/S1 value is the tooth ratio of theplanetary gear set 820; the R2/S2 value is the tooth ratio of theplanetary gear set 830; and the R3/S3 value is the tooth ratio of theplanetary gear set 840. It can be readily recognized from the truthtable that all of the single step forward interchanges are singletransition ratio interchanges. FIG. 9b also describes the ratio stepsbetween adjacent forward ratios and between the reverse and firstforward ratio. For example, the ratio step between the first and secondforward ratios is 1.96.

[0181] Those skilled in the art of planetary transmissions willrecognize that the numerical value of the reverse speed ratio isdetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 840. The numerical value of the first forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 830 and 840. The numerical value of the secondforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 830. The numerical value of the thirdforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 820 and 830. The numerical value ofthe fourth forward speed ratio is 1. The numerical values of the fifthand seventh forward speed ratios are determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 820, 830 and 840.The numerical value of the sixth forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratio of the planetary gear set820.

[0182] The powertrain 910, shown in FIG. 10a, includes the conventionalengine and torque converter 12, a planetary transmission 914, and theconventional final drive mechanism 16. The engine and torque converter12 are drivingly connected with the planetary transmission 914 throughthe input shaft 17. The planetary transmission 914 is drivinglyconnected with the final drive mechanism 16 through the output shaft 19.The planetary transmission 914 includes a planetary gear arrangement 918that has a first planetary gear set 920, a second planetary gear set930, and a third planetary gear set 940.

[0183] The planetary gear set 920 includes a sun gear member 922, a ringgear member 924, and a planet carrier assembly 926. The planet carrierassembly 926 includes a plurality of pinion gears 927 that are rotatablymounted on a carrier member 929 and disposed in meshing relationshipwith the sun gear member 922 and the ring gear member 924, respectively.

[0184] The planetary gear set 930 includes a sun gear member 932, a ringgear member 934, and a planet carrier assembly member 936. The planetcarrier assembly member 936 includes a plurality of pinion gears 937rotatably mounted on a carrier member 939 and disposed in meshingrelationship with both the sun gear member 932 and the ring gear member934.

[0185] The planetary gear set 940 includes a sun gear member 942, a ringgear member 944, and a planet carrier assembly member 946. The planetcarrier assembly member 946 includes a plurality of pinion gears 947rotatably mounted on a carrier member 949 and disposed in meshingrelationship with both the sun gear member 942 and the ring gear member944.

[0186] The planetary gear arrangement 918 also includes sixtorque-transmitting mechanisms 950, 952, 954, 956, 958 and 959. Thetorque-transmitting mechanisms 950, 952, 954, 956 and 958 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanism 959 is a stationary-type torquetransmitting mechanism, commonly termed brake or reaction clutch.

[0187] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 926. The ring gear member 924 iscontinuously connected with the planet carrier assembly member 946through the interconnecting member 970. The planet carrier assemblymember 936 is continuously connected with the ring gear member 944through the interconnecting member 972. The sun gear member 942 iscontinuously connected with the transmission housing 960.

[0188] The planet carrier assembly member 946 is selectively connectablewith the input shaft 17 through the clutch 950. The sun gear member 922is selectively connectable with the input shaft 17 through the clutch952. The ring gear member 934 is selectively connectable with the inputshaft 17 through the clutch 954. The sun gear member 922 is selectivelyconnectable with the sun gear member 932 through the clutch 956. Theplanet carrier assembly member 926 is selectively connectable with theplanet carrier assembly member 936 through the clutch 958. The planetcarrier assembly member 946 is selectively connectable with thetransmission housing 960 through the brake 959.

[0189] The truth table of FIG. 10b describes the torque-transmittingmechanism engagement sequence utilized to provide the reverse speedratio and seven forward speed ratios. The truth table also provides aset of examples for the ratios for each of the reverse and forward speedratios. These numerical values have been determined utilizing the ringgear/sun gear tooth ratios given in FIG. 10b. The R1/S1 value is thetooth ratio of the planetary gear set 920; the R2/S2 value is the toothratio of the planetary gear set 930; and the R3/S3 value is the toothratio of the planetary gear set 940.

[0190] Those skilled in the art, upon reviewing the engagementcombinations, will recognize that the numerical value of the reversespeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 920 and 930. The numerical value of the firstforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 920. The numerical values of the secondand third forward speed ratios are determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 920 and 940. Thenumerical value of the fourth forward speed ratio is 1. The numericalvalues of the fifth and seventh forward speed ratios are determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets920, 930 and 940. The numerical value of the sixth forward speed ratiois determined utilizing the ring gear/sun gear tooth ratio of theplanetary gear set 940.

[0191] A powertrain 1010, shown in FIG. 11a, includes the conventionalengine and torque converter 12, a planetary transmission 1014, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1014 through theinput shaft 17. The planetary transmission 1014 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1014 includes a planetary gear arrangement 1018that has a first planetary gear set 1020, a second planetary gear set1030, and a third planetary gear set 1040.

[0192] The planetary gear set 1020 includes a sun gear member 1022, aring gear member 1024, and a planet carrier assembly 1026. The planetcarrier assembly 1026 includes a plurality of pinion gears 1027rotatably mounted on a carrier member 1029 and disposed in meshingrelationship with both the sun gear member 1022 and the ring gear member1024.

[0193] The planetary gear set 1030 includes a sun gear member 1032, aring gear member 1034, and a planet carrier assembly member 1036. Theplanet carrier assembly member 1036 includes a plurality of pinion gears1037 rotatably mounted on a carrier member 1039 and disposed in meshingrelationship with both the sun gear member 1032 and the ring gear member1034.

[0194] The planetary gear set 1040 includes a sun gear member 1042, aring gear member 1044, and a planet carrier assembly member 1046. Theplanet carrier assembly member 1046 includes a plurality of pinion gears1047 rotatably mounted on a carrier member 1049 and disposed in meshingrelationship with both the sun gear member 1042 and the ring gear member1044.

[0195] The planetary gear arrangement 1018 also includes sixtorque-transmitting mechanisms 1050, 1052, 1054, 1056, 1058 and 1059.The torque-transmitting mechanisms 1050, 1052, 1054, 1056 and 1058 arerotating type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanism 1059 is a stationary-type torquetransmitting mechanism, commonly termed brake or reaction clutch.

[0196] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 1026. The ring gear member 1024is continuously connected with the ring gear member 1044 through theinterconnecting member 1070. The planet carrier assembly member 1036 iscontinuously connected with the planet carrier assembly member 1046through the interconnecting member 1072. The sun gear member 1042 iscontinuously connected with the transmission housing 1060.

[0197] The sun gear member 1022 is selectively connectable with theinput shaft 17 through the clutch 1050. The ring gear member 1034 isselectively connectable with the input shaft 17 through the clutch 1052.The sun gear member 1022 is selectively connectable with the sun gearmember 1032 through the clutch 1054. The planet carrier assembly member1026 is selectively connectable with the sun gear member 1032 throughthe clutch 1056. The ring gear member 1044 is selectively connectablewith the transmission housing 1060 through the brake 1058. The ring gearmember 1034 is selectively connectable with the transmission housing1060 through the brake 1059.

[0198] The truth table shown in FIG. 11b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and the seven forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 11b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 11b. The R1/S1 value is the tooth ratiofor the planetary gear set 1020; the R2/S2 value is the tooth ratio forthe planetary gear set 1030; and the R3/S3 value is the tooth ratio forthe planetary gear set 1040. Also given in FIG. 11b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0199] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 1030. The numerical value ofthe first forward speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 1020. The numerical values ofthe second, third and sixth forward speed ratios are determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets1020, 1030 and 1040. The numerical value of the fourth forward speedratio is 1. The numerical value of the fifth forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1020 and 1040. The numerical value of the seventhforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 1030 and 1040.

[0200] A powertrain 1110, shown in FIG. 12a, has a conventional engineand torque converter 12, a planetary transmission 1114, and theconventional final drive mechanism 16. The planetary transmission 1114includes a planetary gear arrangement 1118 which is connected with theengine and torque converter 12 through the input shaft 17 and with thefinal drive mechanism 16 through the output shaft 19. The planetary geararrangement 1118 includes three planetary gear sets 1120, 1130 and 1140.

[0201] The planetary gear set 1120 includes a sun gear member 1122, aring gear member 1124, and a planet carrier assembly 1126. The planetcarrier assembly 1126 includes a plurality of pinion gears 1127rotatably mounted on a carrier member 1129 and disposed in meshingrelationship with both the sun gear member 1122 and the ring gear member1124.

[0202] The planetary gear set 1130 includes a sun gear member 1132, aring gear member 1134, and a planet carrier assembly member 1136. Theplanet carrier assembly member 1136 includes a plurality of intermeshingpinion gears 1137 that are rotatably mounted on a carrier member 1139and disposed in meshing relationship with both the sun gear member 1132and the ring gear member 1134.

[0203] The planetary gear set 1140 includes a sun gear member 1142, aring gear member 1144, and a planet carrier assembly member 1146. Theplanet carrier assembly member 1146 includes a plurality of pinion gears1147 rotatably mounted on a carrier member 1149 and disposed in meshingrelationship with both the sun gear member 1142 and the ring gear member1144.

[0204] The planetary gear arrangement 1118 also includes sixtorque-transmitting mechanisms 1150, 1152, 1154, 1156, 1158 and 1159.The torque-transmitting mechanisms 1150, 1152, 1154, 1156 and 1158 arerotating type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanism 1159 is a stationary-type torquetransmitting mechanism, commonly termed brake or reaction clutch.

[0205] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 1126. The ring gear member 1124is continuously connected with the planet carrier assembly member 1136through the interconnecting member 1170. The sun gear member 1132 iscontinuously connected with the planet carrier assembly member 1146through the interconnecting member 1172. The ring gear member 1134 iscontinuously connected with the transmission housing 1160.

[0206] The planet carrier assembly member 1136 is selectivelyconnectable with the input shaft 17 through the clutch 1150. The ringgear member 1144 is selectively connectable with the input shaft 17through the clutch 1152. The planet carrier assembly member 1126 isselectively connectable with the sun gear member 1132 through the clutch1154. The sun gear member 1122 is selectively connectable with the ringgear member 1144 through the clutch 1156. The sun gear member 1122 isselectively connectable with the sun gear member 1142 through the clutch1158. The ring gear member 1124 is selectively connectable with thetransmission housing 1160 through the brake 1159.

[0207] The truth table shown in FIG. 12b describes the engagementsequence and engagement combinations utilized with the present familymember to provide the reverse drive ratio and seven forward speedratios. The truth table of FIG. 12b also provides a set of examplenumbers that can be established in the planetary gear arrangement 1118utilizing the ring gear/sun gear tooth ratios. The R1/S1 value is thering gear/sun gear tooth ratio of the planetary gear set 1120; the R2/S2value is the ring gear/sun gear tooth ratio of the planetary gear set1130; and the R3/S3 value is the ring gear/sun gear tooth ratio of theplanetary gear set 1140.

[0208] The chart of FIG. 12b describes the ratio steps between adjacentforward speed ratios for a seven-speed transmission. These step ratiosare established utilizing the example speed ratios given in the truthtable.

[0209] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 1120 and 1140. Thenumerical value of first forward speed ratio is determined utilizing thering gear/sun gear tooth ratio of the planetary gear set 1120. Thenumerical values of the second, third and fifth forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1120 and 1130. The numerical value of the fourthforward speed ratio is 1. The numerical value of the sixth forward speedratio is determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1120, 1130 and 1140. The numerical value of theseventh forward speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 1130.

[0210] A powertrain 1210, shown in FIG. 13a, includes the conventionalengine and torque converter 12, a planetary transmission 1214, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1214 through theinput shaft 17. The planetary transmission 1214 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1214 includes a planetary gear arrangement 1218that has a first planetary gear set 1220, a second planetary gear set1230, and a third planetary gear set 1240.

[0211] The planetary gear set 1220 includes a sun gear member 1222, aring gear member 1224, and a planet carrier assembly 1226. The planetcarrier assembly 1226 includes a plurality of pinion gears 1227rotatably mounted on a carrier member 1229 and disposed in meshingrelationship with both the sun gear member 1222 and the ring gear member1224.

[0212] The planetary gear set 1230 includes a sun gear member 1232, aring gear member 1234, and a planet carrier assembly member 1236. Theplanet carrier assembly member 1236 includes a plurality of pinion gears1237 rotatably mounted on a carrier member 1239 and disposed in meshingrelationship with both the sun gear member 1232 and the ring gear member1234.

[0213] The planetary gear set 1240 includes a sun gear member 1242, aring gear member 1244, and a planet carrier assembly member 1246. Theplanet carrier assembly member 1246 includes a plurality of pinion gears1247 rotatably mounted on a carrier member 1249 and disposed in meshingrelationship with both the sun gear member 1242 and the ring gear member1244.

[0214] The planetary gear arrangement 1218 also includes six torquetransmitting mechanisms 1250, 1252, 1254, 1256, 1258 and 1259. Thetorque-transmitting mechanisms 1250, 1252, 1254 and 1256 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 1258 and 1259 are stationary-type torquetransmitting mechanisms, commonly termed brakes or reaction clutches.

[0215] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 1246. The ring gear member 1224is continuously connected with the ring gear member 1244 through theinterconnecting member 1270. The planet carrier assembly member 1226 iscontinuously connected with the planet carrier assembly member 1236through the interconnecting member 1272. The sun gear member 1222 iscontinuously connected with the transmission housing 1260.

[0216] The ring gear member 1234 is selectively connectable with theinput shaft 17 through the clutch 1250. The sun gear member 1242 isselectively connectable with the input shaft 17 through the clutch 1252.The sun gear member 1232 is selectively connectable with the sun gearmember 1242 through the clutch 1254. The sun gear member 1232 isselectively connectable with the planet carrier assembly member 1246through the clutch 1256. The planet carrier assembly member 1226 isselectively connectable with the transmission housing 1260 through thebrake 1258. The ring gear member 1234 is selectively connectable withthe transmission housing 1260 through the brake 1259.

[0217] The truth table shown in FIG. 13b describes the engagementcombinations and the engagement sequence necessary to provide a reversespeed ratio and seven forward speed ratios. A sample of the numericalvalues for the ratios is also provided in the truth table of FIG. 13b.These values are determined utilizing the ring gear/sun gear toothratios also given in FIG. 13b. The R1/S1 value is the tooth ratio forthe planetary gear set 1220; the R2/S2 value is the tooth ratio for theplanetary gear set 1230; and the R3/S3 value is the tooth ratio for theplanetary gear set 1240. Also given in FIG. 13b is a chart describingthe step ratios between the adjacent forward speed ratios and thereverse to first forward speed ratio.

[0218] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 1230 and 1240. Thenumerical value of the first forward speed ratio is determined utilizingthe ring gear/sun gear tooth ratio of the planetary gear set 1240. Thenumerical values of the second, third and sixth forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1220, 1230 and 1240. The numerical value of thefourth forward speed ratio is 1. The numerical value of the fifthforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 1220 and 1240. The numerical value ofthe seventh forward speed ratio is determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1220 and 1230.

[0219] A powertrain 1310, shown in FIG. 14a, includes the conventionalengine and torque converter 12, a planetary transmission 1314, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1314 through theinput shaft 17. The planetary transmission 1314 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1314 includes a planetary gear arrangement 1318that has a first planetary gear set 1320, a second planetary gear set1330, and a third planetary gear set 1340.

[0220] The planetary gear set 1320 includes a sun gear member 1322, aring gear member 1324, and a planet carrier assembly 1326. The planetcarrier assembly 1326 includes a plurality of pinion gears 1327rotatably mounted on a carrier member 1329 and disposed in meshingrelationship with both the sun gear member 1322 and the ring gear member1324.

[0221] The planetary gear set 1330 includes a sun gear member 1332, aring gear member 1334, and a planet carrier assembly member 1336. Theplanet carrier assembly member 1336 includes a plurality of pinion gears1337 rotatably mounted on a carrier member 1339 and disposed in meshingrelationship with both the sun gear member 1332 and the ring gear member1334.

[0222] The planetary gear set 1340 includes a sun gear member 1342, aring gear member 1344, and a planet carrier assembly member 1346. Theplanet carrier assembly member 1346 includes a plurality of pinion gears1347 rotatably mounted on a carrier member 1349 and disposed in meshingrelationship with both the sun gear member 1342 and the ring gear member1344.

[0223] The planetary gear arrangement 1318 also includes six torquetransmitting mechanisms 1350, 1352, 1354, 1356, 1358 and 1359 each ofwhich is a rotating type torque-transmitting mechanism, commonly termedclutch.

[0224] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 1346. The planet carrierassembly member 1336 is continuously connected with the ring gear member1344 through the interconnecting member 1370. The sun gear member 1322is continuously connected with the sun gear member 1332 through theinterconnecting member 1372. The ring gear member 1334 is continuouslyconnected with the transmission housing 1360.

[0225] The ring gear member 1324 is selectively connectable with theinput shaft 17 through the clutch 1350. The planet carrier assemblymember 1336 is selectively connectable with the input shaft 17 throughthe clutch 1352. The sun gear member 1342 is selectively connectablewith the input shaft 17 through the clutch 1354. The sun gear member1332 is selectively connectable with the planet carrier assembly member1346 through the clutch 1356. The planet carrier assembly member 1326 isselectively connectable with the sun gear member 1342 through the clutch1358. The planet carrier assembly member 1326 is selectively connectablewith the planet carrier assembly member 1346 through the clutch 1359.

[0226] The truth table shown in FIG. 14b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and seven forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 14b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 14b. The R1/S1 value is the tooth ratiofor the planetary gear set 1320; the R2/S2 value is the tooth ratio forthe planetary gear set 1330; and the R3/S3 value is the tooth ratio forthe planetary gear set 1340. Also given in FIG. 14b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0227] Those skilled in the art will recognize that the numerical valuesof the reverse, first and fifth forward speed ratios are determinedutilizing the ring gear/sun gear tooth ratios of the planetary gear sets1320, 1330 and 1340. The numerical values of the second and thirdforward speed ratios are determined utilizing the ring gear/sun geartooth ratios of the planetary gear set 1330 and 1340. The numericalvalue of the fourth forward speed ratio is 1. The numerical value of thesixth forward speed ratio is determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 1320 and 1330. The numericalvalue of the seventh forward speed ratio is determined utilizing thering gear/sun gear tooth ratio of the planetary gear set 1330.

[0228] A powertrain 1410, shown in FIG. 15a, includes the conventionalengine and torque converter 12, a planetary transmission 1414, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1414 through theinput shaft 17. The planetary transmission 1414 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1414 includes a planetary gear arrangement 1418that has a first planetary gear set 1420, a second planetary gear set1430, and a third planetary gear set 1440.

[0229] The planetary gear set 1420 includes a sun gear member 1422, aring gear member 1424, and a planet carrier assembly 1426. The planetcarrier assembly 1426 includes a plurality of pinion gears 1427rotatably mounted on a carrier member 1429 and disposed in meshingrelationship with both the sun gear member 1422 and the ring gear member1424.

[0230] The planetary gear set 1430 includes a sun gear member 1432, aring gear member 1434, and a planet carrier assembly member 1436. Theplanet carrier assembly member 1436 includes a plurality of pinion gears1437 rotatably mounted on a carrier member 1439 and disposed in meshingrelationship with both the sun gear member 1432 and the ring gear member1434.

[0231] The planetary gear set 1440 includes a sun gear member 1442, aring gear member 1444, and a planet carrier assembly member 1446. Theplanet carrier assembly member 1446 includes a plurality of pinion gears1447 rotatably mounted on a carrier member 1449 and disposed in meshingrelationship with both the sun gear member 1442 and the ring gear member1444.

[0232] The planetary gear arrangement 1418 also includes six torquetransmitting mechanisms 1450, 1452, 1454, 1456, 1458 and 1459. Thetorque-transmitting mechanisms 1450, 1452, 1454 and 1456 are rotatingtype torque-transmitting mechanisms, commonly termed clutches. Thetorque-transmitting mechanisms 1458 and 1459 are stationary-type torquetransmitting mechanisms, commonly termed brakes or reaction clutches

[0233] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the sun gear member 1442. The planet carrier assembly member 1426is continuously connected with the ring gear member 1444 through theinterconnecting member 1470. The ring gear member 1424 is continuouslyconnected with the ring gear member 1434 through the interconnectingmember 1472. The sun gear member 1422 is continuously connected with thetransmission housing 1460.

[0234] The planet carrier assembly member 1436 is selectivelyconnectable with the input shaft 17 through the clutch 1450. The sungear member 1432 is selectively connectable with the input shaft 17through the clutch 1452. The planet carrier assembly member 1436 isselectively connectable with the planet carrier assembly member 1446through the clutch 1454. The sun gear member 1432 is selectivelyconnectable with the sun gear member 1442 through the clutch 1456. Thering gear member 1424 is selectively connectable with the transmissionhousing 1460 through the brake 1458. The planet carrier assembly member1446 is selectively connectable with the transmission housing 1460through the brake 1459.

[0235] The truth table shown in FIG. 15b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and seven forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 15b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 15b. The R1/S1 value is the tooth ratiofor the planetary gear set 1420; the R2/S2 value is the tooth ratio forthe planetary gear set 1430; and the R3/S3 value is the tooth ratio forthe planetary gear set 1440. Also given in FIG. 15b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0236] Those skilled in the art will recognize that the numerical valuesof the reverse and fourth forward speed ratios are determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 1420 and1440. The numerical values of the first and fifth forward speed ratiosare determined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1420, 1430 and 1440. The numerical value of thesecond forward speed ratio is determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 1430 and 1440. Thenumerical value of the third forward speed ratio is 1. The numericalvalue of sixth forward speed ratio is determined utilizing the ringgear/sun gear tooth ratio of the planetary gear set 1440. The numericalvalue of the seventh forward speed ratio is determined utilizing thering gear/sun gear tooth ratio of the planetary gear set 1430.

[0237] A powertrain 1510, shown in FIG. 16a, includes the conventionalengine and torque converter 12, a planetary transmission 1514, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1514 through theinput shaft 17. The planetary transmission 1514 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1514 includes a planetary gear arrangement 1518that has a first planetary gear set 1520, a second planetary gear set1530, and a third planetary gear set 1540.

[0238] The planetary gear set 1520 includes a sun gear member 1522, aring gear member 1524, and a planet carrier assembly 1526. The planetcarrier assembly 1526 includes a plurality of pinion gears 1527rotatably mounted on a carrier member 1529 and disposed in meshingrelationship with both the sun gear member 1522 and the ring gear member1524.

[0239] The planetary gear set 1530 includes a sun gear member 1532, aring gear member 1534, and a planet carrier assembly member 1536. Theplanet carrier assembly member 1536 includes a plurality of pinion gears1537 rotatably mounted on a carrier member 1539 and disposed in meshingrelationship with both the sun gear member 1532 and the ring gear member1534.

[0240] The planetary gear set 1540 includes a sun gear member 1542, aring gear member 1544, and a planet carrier assembly member 1546. Theplanet carrier assembly member 1546 includes a plurality of pinion gears1547 rotatably mounted on a carrier member 1549 and disposed in meshingrelationship with both the sun gear member 1542 and the ring gear member1544.

[0241] The planetary gear arrangement 1518 also includes six torquetransmitting mechanisms 1550, 1552, 1554, 1556, 1558 and 1559. Thetorque-transmitting mechanisms 1550, 1552, 1554, 1556 and 1558 arerotating type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanism 1559 is a stationary-typetorque-transmitting mechanism, commonly termed brake or reaction clutch.

[0242] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the ring gear member 1524. The planet carrier assembly member 1526is continuously connected with the ring gear member 1544 through theinterconnecting member 1570. The planet carrier assembly member 1536 iscontinuously connected with the planet carrier assembly member 1546through the interconnecting member 1572. The sun gear member 1542 iscontinuously connected with the transmission housing 1560.

[0243] The planet carrier assembly member 1526 is selectivelyconnectable with the input shaft 17 through the clutch 1550. The sungear member 1522 is selectively connectable with the input shaft 17through the clutch 1552. The ring gear member 1534 is selectivelyconnectable with the input shaft 17 through the clutch 1554. The planetcarrier assembly member 1526 is selectively connectable with the sungear member 1532 through the clutch 1556. The sun gear member 1522 isselectively connectable with the sun gear member 1532 through the clutch1558. The ring gear member 1534 is selectively connectable with thetransmission housing 1560 through the brake 1559.

[0244] The truth table shown in FIG. 16b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and the seven forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 16b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 16b. The R1/S1 value is the tooth ratiofor the planetary gear set 1520; the R2/S2 value is the tooth ratio forthe planetary gear set 1530; and the R3/S3 value is the tooth ratio forthe planetary gear set 1540. Also given in FIG. 16b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0245] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 1520. The numerical values ofthe first, second, fourth and seventh forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1520, 1530 and 1540. The numerical value of thethird forward speed ratio is 1. The numerical value of the fifth forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear sets 1520 and 1540. The numerical value of thesixth forward speed ratio is determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 1530 and 1540.

[0246] A powertrain 1610, shown in FIG. 17a, includes the conventionalengine and torque converter 12, a planetary transmission 1614, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1614 through theinput shaft 17. The planetary transmission 1614 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1614 includes a planetary gear arrangement 1618that has a first planetary gear set 1620, a second planetary gear set1630, and a third planetary gear set 1640.

[0247] The planetary gear set 1620 includes a sun gear member 1622, aring gear member 1624, and a planet carrier assembly 1626. The planetcarrier assembly 1626 includes a plurality of pinion gears 1627rotatably mounted on a carrier member 1629 and disposed in meshingrelationship with both the sun gear member 1622 and the ring gear member1624.

[0248] The planetary gear set 1630 includes a sun gear member 1632, aring gear member 1634, and a planet carrier assembly member 1636. Theplanet carrier assembly member 1636 includes a plurality of pinion gears1637 rotatably mounted on a carrier member 1639 and disposed in meshingrelationship with both the sun gear member 1632 and the ring gear member1634.

[0249] The planetary gear set 1640 includes a sun gear member 1642, aring gear member 1644, and a planet carrier assembly member 1646. Theplanet carrier assembly member 1646 includes a plurality of pinion gears1647 rotatably mounted on a carrier member 1649 and disposed in meshingrelationship with both the sun gear member 1642 and the ring gear member1644.

[0250] The planetary gear arrangement 1618 also includes six torquetransmitting mechanisms 1650, 1652, 1654, 1656, 1658 and 1659 each ofwhich is a rotating-type torque-transmitting mechanism, commonly termedclutch.

[0251] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 1646. The sun gear member 1622is continuously connected with the ring gear member 1644 through theinterconnecting member 1670. The planet carrier assembly member 1626 iscontinuously connected with the sun gear member 1632 through theinterconnecting member 1672. The ring gear member 1624 is continuouslyconnected with the transmission housing 1660.

[0252] The planet carrier assembly member 1626 is selectivelyconnectable with the input shaft 17 through the clutch 1650. The sungear member 1642 is selectively connectable with the input shaft 17through the clutch 1652. The ring gear member 1634 is selectivelyconnectable with the planet carrier assembly member 1636 through theclutch 1654. The sun gear member 1622 is selectively connectable withthe planet carrier assembly member 1636 through the clutch 1656. Theplanet carrier assembly member 1636 is selectively connectable with thesun gear member 1642 through the clutch 1658. The ring gear member 1634is selectively connectable with the planet carrier assembly member 1646through the clutch 1659.

[0253] The truth table shown in FIG. 17b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and the eight forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 17b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 17b. The R1/S1 value is the tooth ratiofor the planetary gear set 1620; the R2/S2 value is the tooth ratio forthe planetary gear set 1630; and the R3/S3 value is the tooth ratio forthe planetary gear set 1640. Also given in FIG. 17b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0254] Those skilled in the art will recognize that the numerical valuesof the reverse and fifth forward speed ratios are determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 1620 and1640. The numerical value of the first forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratio of the planetary gear set1640. The numerical values of the second, fourth and sixth forward speedratios are determined utilizing the ring gear/sun gear tooth ratios ofthe planetary gear sets 1620, 1630 and 1640. The numerical value of thethird forward speed ratio is 1. The numerical value of the seventhforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 1620. The numerical value of the eighthforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 1620 and 1630.

[0255] A powertrain 1710, shown in FIG. 18a, includes the conventionalengine and torque converter 12, a planetary transmission 1714, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 1714 through theinput shaft 17. The planetary transmission 1714 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 1714 includes a planetary gear arrangement 1718that has a first planetary gear set 1720, a second planetary gear set1730, and a third planetary gear set 1740.

[0256] The planetary gear set 1720 includes a sun gear member 1722, aring gear member 1724, and a planet carrier assembly 1726. The planetcarrier assembly 1726 includes a plurality of pinion gears 1727rotatably mounted on a carrier member 1729 and disposed in meshingrelationship with both the sun gear member 1722 and the ring gear member1724.

[0257] The planetary gear set 1730 includes a sun gear member 1732, aring gear member 1734, and a planet carrier assembly member 1736. Theplanet carrier assembly member 1736 includes a plurality of pinion gears1737 rotatably mounted on a carrier member 1739 and disposed in meshingrelationship with both the sun gear member 1732 and the ring gear member1734.

[0258] The planetary gear set 1740 includes a sun gear member 1742, aring gear member 1744, and a planet carrier assembly member 1746. Theplanet carrier assembly member 1746 includes a plurality of pinion gears1747 rotatably mounted on a carrier member 1749 and disposed in meshingrelationship with both the sun gear member 1742 and the ring gear member1744.

[0259] The planetary gear arrangement 1718 also includes six torquetransmitting mechanisms 1750, 1752, 1754, 1756, 1758 and 1759. Thetorque-transmitting mechanisms 1750, 1752, 1754, 1756 and 1758 arerotating-type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanism 1759 is a stationary-typetorque-transmitting mechanism, commonly termed brake or reaction clutch.

[0260] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 1726. The sun gear member 1732is continuously connected with the ring gear member 1744 through theinterconnecting member 1770. The sun gear member 1722 is continuouslyconnected with the planet carrier assembly member 1746 through theinterconnecting member 1772. The sun gear member 1742 is continuouslyconnected with the transmission housing 1760.

[0261] The planet carrier assembly member 1746 is selectivelyconnectable with the input shaft 17 through the clutch 1750. The ringgear member 1734 is selectively connectable with the input shaft 17through the clutch 1752. The planet carrier assembly member 1736 isselectively connectable with the input shaft 17 through the clutch 1754.The ring gear member 1724 is selectively connectable with the ring gearmember 1734 through the clutch 1756. The ring gear member 1724 isselectively connectable with the planet carrier assembly member 1736through the clutch 1758. The ring gear member 1724 is selectivelyconnectable with the transmission housing 1760 through the brake 1759.

[0262] The truth table shown in FIG. 18b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and eight forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 18b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 18b. The R1/S1 value is the tooth ratiofor the planetary gear set 1720; the R2/S2 value is the tooth ratio forthe planetary gear set 1730; and the R3/S3 value is the tooth ratio forthe planetary gear set 1740. Also given in FIG. 18b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0263] Those skilled in the art will recognize that the numerical valuesof the reverse, third, fourth and seventh forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1720, 1730 and 1740. The numerical values of thefirst, fifth and eighth forward speed ratios are determined utilizingthe ring gear/sun gear tooth ratios of the planetary gear sets 1720 and1740. The numerical value of the second forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 1720. The numerical value of the sixth forward speed ratio is1.

[0264] A powertrain 1810, shown in FIG. 19a, has the conventional engineand torque converter 12, a planetary transmission 1814, and the finaldrive mechanism 16. The engine and torque converter 12 are drivinglyconnected with the planetary transmission 1814 through the input shaft17. The planetary transmission 1814 is drivingly connected with thefinal drive mechanism 16 through the output shaft 19. The planetarytransmission 1814 includes a planetary gear arrangement 1818 that has afirst planetary gear set 1820, a second planetary gear set 1830, and athird planetary gear set 1840.

[0265] The planetary gear set 1820 includes a sun gear member 1822, aring gear member 1824, and a planet carrier assembly 1826. The planetcarrier assembly 1826 includes a plurality of pinion gears 1827rotatably mounted on a carrier member 1829 and disposed in meshingrelationship with both the sun gear member 1822 and the ring gear member1824.

[0266] The planetary gear set 1830 includes a sun gear member 1832, aring gear member 1834, and a planet carrier assembly member 1836. Theplanet carrier assembly member 1836 includes a plurality of pinion gears1837 rotatably mounted on a carrier member 1839 and disposed in meshingrelationship with both the sun gear member 1832 and the ring gear member1834.

[0267] The planetary gear set 1840 includes a sun gear member 1842, aring gear member 1844, and a planet carrier assembly member 1846. Theplanet carrier assembly member 1846 includes a plurality of pinion gears1847 rotatably mounted on a carrier member 1849 and disposed in meshingrelationship with both the sun gear member 1842 and the ring gear member1844.

[0268] The planetary gear arrangement 1818 also includes sixtorque-transmitting mechanisms 1850, 1852, 1854, 1856, 1858 and 1859.The torque-transmitting mechanisms 1850, 1852, 1854, 1856 and 1858 arerotating type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanism 1859 is a stationary-type torquetransmitting mechanism, commonly termed brake or reaction clutch.

[0269] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 1826. The sun gear member 1822is continuously connected with the ring gear member 1834 through theinterconnecting member 1870. The planet carrier assembly member 1836 iscontinuously connected with the ring gear member 1844 through theinterconnecting member 1872. The sun gear member 1832 is continuouslyconnected with the transmission housing 1860.

[0270] The ring gear member 1824 is selectively connectable with theinput shaft 17 through the clutch 1850. The sun gear member 1842 isselectively connectable with the input shaft 17 through the clutch 1852.The ring gear member 1834 is selectively connectable with the planetcarrier assembly member 1846 through the clutch 1854. The ring gearmember 1824 is selectively connectable with the planet carrier assemblymember 1846 through the clutch 1856. The planet carrier assembly member1826 is selectively connectable with the planet carrier assembly member1836 through the clutch 1858. The ring gear member 1824 is selectivelyconnectable with the transmission housing 1860 through the brake 1859.

[0271] The truth table shown in FIG. 19b defines the torque-transmittingmechanism engagement sequence that provides the reverse speed ratio andeight forward speed ratios shown in the truth table and available withthe planetary gear arrangement 1818. The truth table indicates that thetorque-transmitting mechanisms 1852 and 1859 can remain engaged throughthe neutral condition, thereby simplifying the forward/reverseinterchange. A sample of numerical values for the individual ratios isalso given in the truth table of FIG. 19b. These numerical values havebeen calculated using the ring gear/sun gear tooth ratios also given byway of example in FIG. 19b. The R1/S1 value is the tooth ratio of theplanetary gear set 1820; the R2/S2 value is the tooth ratio of theplanetary gear set 1830; and the R3/S3 value is the tooth ratio of theplanetary gear set 1840. It can be readily recognized from the truthtable that all of the single and double step forward interchanges aresingle transition ratio interchanges. FIG. 19b also describes the ratiosteps between adjacent forward ratios and between the reverse and firstforward ratio. For example, the ratio step between the first and secondforward ratios is 2.03.

[0272] Those skilled in the art of planetary transmissions willrecognize that the numerical values of the reverse, first, fourth andeighth forward speed ratios are determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 1820, 1830 and 1840. Thenumerical values of the second and third forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1830 and 1840. The numerical value of the fifthforward speed ratio is 1. The numerical values of the sixth and seventhforward speed ratios are determined utilizing the ring gear/sun geartooth ratios of the planetary gear sets 1820 and 1830.

[0273] The powertrain 1910, shown in FIG. 20a, includes the conventionalengine and torque converter 12, a planetary transmission 1914, and theconventional final drive mechanism 16. The engine and torque converter12 are drivingly connected with the planetary transmission 1914 throughthe input shaft 17. The planetary transmission 1914 is drivinglyconnected with the final drive mechanism 16 through the output shaft 19.The planetary transmission 1914 includes a planetary gear arrangement1918 that has a first planetary gear set 1920, a second planetary gearset 1930, and a third planetary gear set 1940.

[0274] The planetary gear set 1920 includes a sun gear member 1922, aring gear member 1924, and a planet carrier assembly 1926. The planetcarrier assembly 1926 includes a plurality of pinion gears 1927 that arerotatably mounted on a carrier member 1929 and disposed in meshingrelationship with the sun gear member 1922 and the ring gear member1924, respectively.

[0275] The planetary gear set 1930 includes a sun gear member 1932, aring gear member 1934, and a planet carrier assembly member 1936. Theplanet carrier assembly member 1936 includes a plurality of pinion gears1937 rotatably mounted on a carrier member 1939 and disposed in meshingrelationship with both the sun gear member 1932 and the ring gear member1934.

[0276] The planetary gear set 1940 includes a sun gear member 1942, aring gear member 1944, and a planet carrier assembly member 1946. Theplanet carrier assembly member 1946 includes a plurality of pinion gears1947 rotatably mounted on a carrier member 1949 and disposed in meshingrelationship with both the sun gear member 1942 and the ring gear member1944.

[0277] The planetary gear arrangement 1918 also includes sixtorque-transmitting mechanisms 1950, 1952, 1954, 1956, 1958 and 1959each of which is a rotating type torque-transmitting mechanism, commonlytermed clutch.

[0278] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the ring gear member 1944. The sun gear member 1922 is continuouslyconnected with the planet carrier assembly member 1936 through theinterconnecting member 1970. The sun gear member 1932 is continuouslyconnected with the sun gear member 1942 through the interconnectingmember 1972. The ring gear member 1934 is continuously connected withthe transmission housing 1960.

[0279] The ring gear member 1924 is selectively connectable with theinput shaft 17 through the clutch 1950. The planet carrier assemblymember 1926 is selectively connectable with the input shaft 17 throughthe clutch 1952. The planet carrier assembly member 1946 is selectivelyconnectable with the input shaft 17 through the clutch 1954. The planetcarrier assembly member 1936 is selectively connectable with the ringgear member 1944 through the clutch 1956. The ring gear member 1924 isselectively connectable with the sun gear member 1932 through the clutch1958. The planet carrier assembly member 1926 is selectively connectablewith the sun gear member 1932 through the clutch 1959.

[0280] The truth table of FIG. 20b describes the torque-transmittingmechanism engagement sequence utilized to provide the reverse speedratio and eight forward speed ratios. The truth table also provides aset of examples for the ratios for each of the reverse and forward speedratios. These numerical values have been determined utilizing the ringgear/sun gear tooth ratios given in FIG. 20b. The R1/S1 value is thetooth ratio of the planetary gear set 1920; the R2/S2 value is the toothratio of the planetary gear set 1930; and the R3/S3 value is the toothratio of the planetary gear set 1940.

[0281] Those skilled in the art, upon reviewing the engagementcombinations, will recognize that the numerical values of the reverseand fourth forward speed ratios are determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1930 and 1940. Thenumerical values of the first and third forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 1920 and 1930. The numerical value of the secondforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 1930. The numerical values of the fifthand seventh forward speed ratio are determined utilizing the ringgear/sun gear tooth ratios of the planetary gear sets 1920, 1930 and1940. The numerical value of the sixth forward speed ratio is 1. Thenumerical value of the eighth forward speed ratio is determinedutilizing the ring gear/sun gear tooth ratio of the planetary gear set1940.

[0282] A powertrain 2010, shown in FIG. 21a, includes the conventionalengine and torque converter 12, a planetary transmission 2014, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 2014 through theinput shaft 17. The planetary transmission 2014 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 2014 includes a planetary gear arrangement 2018that has a first planetary gear set 2020, a second planetary gear set2030, and a third planetary gear set 2040.

[0283] The planetary gear set 2020 includes a sun gear member 2022, aring gear member 2024, and a planet carrier assembly 2026. The planetcarrier assembly 2026 includes a plurality of pinion gears 2027rotatably mounted on a carrier member 2029 and disposed in meshingrelationship with both the sun gear member 2022 and the ring gear member2024.

[0284] The planetary gear set 2030 includes a sun gear member 2032, aring gear member 2034, and a planet carrier assembly member 2036. Theplanet carrier assembly member 2036 includes a plurality of pinion gears2037 rotatably mounted on a carrier member 2039 and disposed in meshingrelationship with both the sun gear member 2032 and the ring gear member2034.

[0285] The planetary gear set 2040 includes a sun gear member 2042, aring gear member 2044, and a planet carrier assembly member 2046. Theplanet carrier assembly member 2046 includes a plurality of pinion gears2047 rotatably mounted on a carrier member 2049 and disposed in meshingrelationship with both the sun gear member 2042 and the ring gear member2044.

[0286] The planetary gear arrangement 2018 also includes sixtorque-transmitting mechanisms 2050, 2052, 2054, 2056, 2058 and 2059.The torque-transmitting mechanisms 2050, 2052, 2054, 2056 and 2058 arerotating type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanism 2059 is a stationary-type torquetransmitting mechanism, commonly termed brake or reaction clutch.

[0287] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the ring gear member 2044. The ring gear member 2024 iscontinuously connected with the sun gear member 2042 through theinterconnecting member 2070. The sun gear member 2022 is continuouslyconnected with the sun gear member 2032 through the interconnectingmember 2072. The planet carrier assembly member 2026 is continuouslyconnected with the transmission housing 2060.

[0288] The ring gear member 2034 is selectively connectable with theinput shaft 17 through the clutch 2050. The planet carrier assemblymember 2046 is selectively connectable with the input shaft 17 throughthe clutch 2052. The ring gear member 2034 is selectively connectablewith the planet carrier assembly member 2036 through the clutch 2054.The ring gear member 2024 is selectively connectable with the planetcarrier assembly member 2036 through the clutch 2056. The planet carrierassembly member 2046 is selectively connectable with the sun gear member2042 through the clutch 2058. The planet carrier assembly member 2036 isselectively connectable with the transmission housing 2060 through thebrake 2059.

[0289] The truth table shown in FIG. 21b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and the seven forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 21b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 21b. The R1/S1 value is the tooth ratiofor the planetary gear set 2020; the R2/S2 value is the tooth ratio forthe planetary gear set 2030; and the R3/S3 value is the tooth ratio forthe planetary gear set 2040. Also given in FIG. 21b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0290] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 2020. The numerical values ofthe first and second forward speed ratios are determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 2020 and2030. The numerical value of the third forward speed ratio is 1. Thenumerical values of the fourth and fifth forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 2020, 2030 and 2040. The numerical value of sixthforward speed ratio is determined utilizing the ring gear/sun gear toothratio of the planetary gear set 2040. The numerical value of the seventhforward speed ratio is determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 2020 and 2040.

[0291] A powertrain 2110, shown in FIG. 22a, has a conventional engineand torque converter 12, a planetary transmission 2114, and theconventional final drive mechanism 16. The planetary transmission 2114includes a planetary gear arrangement 2118 which is connected with theengine and torque converter 12 through the input shaft 17 and with thefinal drive mechanism 16 through the output shaft 19. The planetary geararrangement 2118 includes three planetary gear sets 2120, 2130 and 2140.

[0292] The planetary gear set 2120 includes a sun gear member 2122, aring gear member 2124, and a planet carrier assembly 2126. The planetcarrier assembly 2126 includes a plurality of pinion gears 2127rotatably mounted on a carrier member 2129 and disposed in meshingrelationship with both the sun gear member 2122 and the ring gear member2124.

[0293] The planetary gear set 2130 includes a sun gear member 2132, aring gear member 2134, and a planet carrier assembly member 2136. Theplanet carrier assembly member 2136 includes a plurality of intermeshingpinion gears 2137 that are rotatably mounted on a carrier member 2139and disposed in meshing relationship with both the sun gear member 2132and the ring gear member 2134.

[0294] The planetary gear set 2140 includes a sun gear member 2142, aring gear member 2144, and a planet carrier assembly member 2146. Theplanet carrier assembly member 2146 includes a plurality of pinion gears2147 rotatably mounted on a carrier member 2149 and disposed in meshingrelationship with both the sun gear member 2142 and the ring gear member2144.

[0295] The planetary gear arrangement 2118 also includes sixtorque-transmitting mechanisms 2150, 2152, 2154, 2156, 2158 and 2159.The torque-transmitting mechanisms 2150, 2152, 2154, 2156 and 2158 arerotating type torque-transmitting mechanisms, commonly termed clutches.The torque-transmitting mechanism 2159 is a stationary-type torquetransmitting mechanism, commonly termed brake or reaction clutch.

[0296] (The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the sun gear member 2142. The ring gear member 2124 is continuouslyconnected with the ring gear member 2144 through the interconnectingmember 2170. The sun gear member 2122 is continuously connected with thesun gear member 2132 through the interconnecting member 2172. The planetcarrier assembly member 2126 is continuously connected with thetransmission housing 2160.

[0297] The ring gear member 2134 is selectively connectable with theinput shaft 17 through the clutch 2150. The planet carrier assemblymember 2146 is selectively connectable with the input shaft 17 throughthe clutch 2152. The ring gear member 2134 is selectively connectablewith the planet carrier assembly member 2136 through the clutch 2154.The ring gear member 2124 is selectively connectable with the planetcarrier assembly member 2136 through the clutch 2156. The ring gearmember 2144 is selectively connectable with the planet carrier assemblymember 2146 through the clutch 2158. The planet carrier assembly member2136 is selectively connectable with the transmission housing 2160through the brake 2159.

[0298] The truth table shown in FIG. 22b describes the engagementsequence and engagement combinations utilized with the present familymember to provide the reverse drive ratio and seven forward speedratios. The truth table of FIG. 22b also provides a set of examplenumbers that can be established in the planetary gear arrangement 2118utilizing the ring gear/sun gear tooth ratios. The R1/S1 value is thering gear/sun gear tooth ratio of the planetary gear set 2120; the R2/S2value is the ring gear/sun gear tooth ratio of the planetary gear set2130; and the R3/S3 value is the ring gear/sun gear tooth ratio of theplanetary gear set 2140.

[0299] The chart of FIG. 22b describes the ratio steps between adjacentforward speed ratios for a seven-speed transmission. These step ratiosare established utilizing the example speed ratios given in the truthtable.

[0300] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 2120. The numerical values ofthe first and second forward speed ratios are determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 2120 and2130. The numerical value of the third forward speed ratio is 1. Thenumerical values of the fourth and fifth forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 2120, 2130 and 2140. The numerical value of thesixth forward speed ratio is determined utilizing the ring gear/sun geartooth ratio of the planetary gear set 2140. The numerical value of theseventh forward speed ratio is determined utilizing the ring gear/sungear tooth ratios of planetary gear sets 2120 and 2140.

[0301] A powertrain 2210, shown in FIG. 23a, includes the conventionalengine and torque converter 12, a planetary transmission 2214, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 2214 through theinput shaft 17. The planetary transmission 2214 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 2214 includes a planetary gear arrangement 2218that has a first planetary gear set 2220, a second planetary gear set2230, and a third planetary gear set 2240.

[0302] The planetary gear set 2220 includes a sun gear member 2222, aring gear member 2224, and a planet carrier assembly 2226. The planetcarrier assembly 2226 includes a plurality of pinion gears 2227rotatably mounted on a carrier member 2229 and disposed in meshingrelationship with both the sun gear member 2222 and the ring gear member2224.

[0303] The planetary gear set 2230 includes a sun gear member 2232, aring gear member 2234, and a planet carrier assembly member 2236. Theplanet carrier assembly member 2236 includes a plurality of pinion gears2237 rotatably mounted on a carrier member 2239 and disposed in meshingrelationship with both the sun gear member 2232 and the ring gear member2234.

[0304] The planetary gear set 2240 includes a sun gear member 2242, aring gear member 2244, and a planet carrier assembly member 2246. Theplanet carrier assembly member 2246 includes a plurality of pinion gears2247 rotatably mounted on a carrier member 2249 and disposed in meshingrelationship with both the sun gear member 2242 and the ring gear member2244.

[0305] The planetary gear arrangement 2218 also includes six torquetransmitting mechanisms 2250, 2252, 2254, 2256, 2258 and 2259 each ofwhich is a rotating type torque-transmitting mechanism, commonly termedclutch.

[0306] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the ring gear member 2224. The planet carrier assembly member 2226is continuously connected with the ring gear member 2234 through theinterconnecting member 2270. The planet carrier assembly member 2236 iscontinuously connected with the sun gear member 2242 through theinterconnecting member 2272. The sun gear member 2232 is continuouslyconnected with the transmission housing 2260.

[0307] The planet carrier assembly member 2226 is selectivelyconnectable with the input shaft 17 through the clutch 2250. The sungear member 2222 is selectively connectable with the input shaft 17through the clutch 2252. The planet carrier assembly member 2236 isselectively connectable with the input shaft 17 through the clutch 2254.The ring gear member 2234 is selectively connectable with the planetcarrier assembly member 2246 through the clutch 2256. The ring gearmember 2224 is selectively connectable with the ring gear member 2244through the clutch 2258. The planet carrier assembly member 2246 isselectively connectable with the sun gear member 2242 through the clutch2259.

[0308] The truth table shown in FIG. 23b describes the engagementcombinations and the engagement sequence necessary to provide a reversespeed ratio and seven forward speed ratios. A sample of the numericalvalues for the ratios is also provided in the truth table of FIG. 23b.These values are determined utilizing the ring gear/sun gear toothratios also given in FIG. 23b. The R1/S1 value is the tooth ratio forthe planetary gear set 2220; the R2/S2 value is the tooth ratio for theplanetary gear set 2230; and the R3/S3 value is the tooth ratio for theplanetary gear set 2240. Also given in FIG. 13b is a chart describingthe step ratios between the adjacent forward speed ratios and thereverse to first forward speed ratio.

[0309] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratio of the planetary gear set 2220. The numerical values ofthe first and seventh forward speed ratios are determined utilizing thering gear/sun gear tooth ratios of the planetary gear sets 2220 and2230. The numerical value of the second forward speed ratio isdetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 2230. The numerical value of third forward speed ratio is 1.The numerical values of the fourth and sixth forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratios of theplanetary gear sets 2230 and 2240. The numerical value of fifth forwardspeed ratio is determined utilizing the ring gear/sun gear tooth ratiosof the planetary gear set 2220, 2230 and 2240.

[0310] A powertrain 2310, shown in FIG. 24a, includes the conventionalengine and torque converter 12, a planetary transmission 2314, and theconventional final drive mechanism 16. The engine and torque converterare drivingly connected with the planetary transmission 2314 through theinput shaft 17. The planetary transmission 2314 is drivingly connectedwith the final drive mechanism 16 through the output shaft 19. Theplanetary transmission 2314 includes a planetary gear arrangement 2318that has a first planetary gear set 2320, a second planetary gear set2330, and a third planetary gear set 2340.

[0311] The planetary gear set 2320 includes a sun gear member 2322, aring gear member 2324, and a planet carrier assembly 2326. The planetcarrier assembly 2326 includes a plurality of pinion gears 2327rotatably mounted on a carrier member 2329 and disposed in meshingrelationship with both the sun gear member 2322 and the ring gear member2324.

[0312] The planetary gear set 2330 includes a sun gear member 2332, aring gear member 2334, and a planet carrier assembly member 2336. Theplanet carrier assembly member 2336 includes a plurality of pinion gears2337 and 2338 rotatably mounted on a carrier member 2339 and disposed inmeshing relationship with both the sun gear member 2332 and the ringgear member 2334.

[0313] The planetary gear set 2340 includes a sun gear member 2342, aring gear member 2344, and a planet carrier assembly member 2346. Theplanet carrier assembly member 2346 includes a plurality of pinion gears2347 rotatably mounted on a carrier member 2349 and disposed in meshingrelationship with both the sun gear member 2342 and the ring gear member2344.

[0314] The planetary gear arrangement 2318 also includes six torquetransmitting mechanisms 2350, 2352, 2354, 2356, 2358 and 2359 each ofwhich is a rotating type torque-transmitting mechanism, commonly termedclutch.

[0315] The input shaft 17 is not continuously connected with anyplanetary gear member. The output shaft 19 is continuously connectedwith the planet carrier assembly member 2326. The sun gear member 2322is continuously connected with the planet carrier assembly member 2346through the interconnecting member 2370. The planet carrier assemblymember 2336 is continuously connected with the sun gear member 2342through the interconnecting member 2372. The ring gear member 2344 iscontinuously connected with the transmission housing 2360.

[0316] The planet carrier assembly member 2346 is selectivelyconnectable with the input shaft 17 through the clutch 2350. The sungear member 2332 is selectively connectable with the input shaft 17through the clutch 2352. The ring gear member 2324 is selectivelyconnectable with the planet carrier assembly member 2326 through theclutch 2354. The planet carrier assembly member 2326 is selectivelyconnectable with the sun gear member 2332 through the clutch 2356. Thering gear member 2324 is selectively connectable with the ring gearmember 2334 through the clutch 2358. The sun gear member 2332 isselectively connectable with the sun gear member 2342 through the clutch2359.

[0317] The truth table shown in FIG. 24b describes the engagementcombinations and the engagement sequence necessary to provide thereverse drive ratio and seven forward speed ratios. A sample of thenumerical values for the ratios is also provided in the truth table ofFIG. 24b. These values are determined utilizing the ring gear/sun geartooth ratios also given in FIG. 24b. The R1/S1 value is the tooth ratiofor the planetary gear set 2320; the R2/S2 value is the tooth ratio forthe planetary gear set 2330; and the R3/S3 value is the tooth ratio forthe planetary gear set 2340. Also given in FIG. 24b is a chartdescribing the step ratios between the adjacent forward speed ratios andthe reverse to first forward speed ratio.

[0318] Those skilled in the art will recognize that the numerical valueof the reverse speed ratio is determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 2330 and 2340. Thenumerical values of the first and seventh forward speed ratios aredetermined utilizing the ring gear/sun gear tooth ratio of the planetarygear set 2340. The numerical values of the second and sixth forwardspeed ratios are determined utilizing the ring gear/sun gear toothratios of the planetary gear sets 2320 and 2340. The numerical value ofthe third forward speed ratio is 1. The numerical values of fourth andfifth forward speed ratios are determined utilizing the ring gear/sungear tooth ratios of the planetary gear sets 2320, 2330 and 2340.

[0319] While the best modes for carrying out the invention have beendescribed in detail, those familiar with the art to which this inventionrelates will recognize various alternative designs and embodiments forpracticing the invention within the scope of the appended claims.

1. A family of transmissions wherein each family member comprises: aninput shaft; an output shaft; first, second and third planetary gearsets each having first, second and third members; said output shaftbeing continuously interconnected with a member of said planetary gearsets, and said input shaft being selectively connectable with members ofsaid planetary gear sets; a first interconnecting member continuouslyinterconnecting said first member of said first planetary gear set withsaid first member of said second planetary gear set; a secondinterconnecting member continuously interconnecting said second memberof said second planetary gear set with said first member of said thirdplanetary gear set; said third member of said second planetary gear setbeing continuously connected with a stationary member (transmissionhousing); a first torque-transmitting mechanism selectivelyinterconnecting a member of said first, second or third planetary gearset with said input shaft; a second torque-transmitting mechanismselectively interconnecting a member of said first, second or thirdplanetary gear set or said first or second interconnecting member withsaid input shaft; a third torque-transmitting mechanism selectivelyinterconnecting a member of said first, second or third planetary gearset with said input shaft, said output shaft or another member of saidfirst, second or third planetary gear set; a fourth torque-transmittingmechanism selectively interconnecting a member of said first or thirdplanetary gear set with another member of said first, second or thirdplanetary gear set; a fifth torque-transmitting mechanism selectivelyinterconnecting a member of said first, second or third planetary gearset with another member of said first, second or third planetary gearset, or said stationary member; and a sixth torque-transmittingmechanism selectively interconnecting a member of the first or thirdplanetary gear set with another member of said first, second or thirdplanetary gear set, or with said stationary member; saidtorque-transmitting mechanisms being engaged in combinations of three toestablish at least seven forward speed ratios and at least one reversespeed ratio between said input shaft and said output shaft.
 2. Thefamily of transmissions defined in claim 1, wherein said first, second,third, fourth, fifth and sixth torque-transmitting mechanisms compriseclutches.
 3. The family of transmissions defined in claim 1, whereinsaid first, second, third, fourth and fifth torque-transmittingmechanisms comprise clutches, and said sixth torque-transmittingmechanism comprises a brake.
 4. The family of transmissions defined inclaim 1, wherein said first, second, third and fourthtorque-transmitting mechanisms comprise clutches, and said fifth andsixth torque-transmitting mechanisms comprise brakes.
 5. The family oftransmissions defined in claim 1, wherein said sixth torque-transmittingmechanism comprises a brake selectively interconnecting a member of saidfirst or third planetary gear set with said stationary member.
 6. Thefamily of transmissions defined in claim 1, wherein planet carrierassembly members of each of said planetary gear sets are of thesingle-pinion type.
 7. The family of transmissions defined in claim 1,wherein at least one planet carrier assembly member of said planetarygear sets is of the double-pinion type.
 8. A family of transmissionshaving a plurality of family members wherein each family membercomprises: an input shaft; an output shaft; a planetary gear arrangementhaving first, second and third planetary gear sets, each planetary gearset having first, second and third members; said output shaft beingcontinuously interconnected with a member of said planetary gear sets,and said input shaft being selectively connectable with members of saidplanetary gear sets; a first interconnecting member continuouslyinterconnecting said first member of said first planetary gear set withsaid first member of said second planetary gear set; a secondinterconnecting member continuously interconnecting said second memberof said second planetary gear set with said first member of said thirdplanetary gear set; said third member of said second planetary gear setbeing continuously connected with a stationary member; and sixtorque-transmitting mechanisms for selectively interconnecting saidmembers of said first, second or third planetary gear sets with saidinput shaft, said output shaft, said first or second interconnectingmember, said stationary member or with other members of said planetarygear sets, said six torque-transmitting mechanisms being engaged incombinations of three to establish at least seven forward speed ratiosand one reverse speed ratio between said input shaft and said outputshaft.
 9. The family of transmissions defined in claim 8, wherein afirst of said six torque-transmitting mechanisms is operable forselectively interconnecting a member of said first, second or thirdplanetary gear set with said input shaft.
 10. The family oftransmissions defined in claim 8, wherein a second of said sixtorque-transmitting mechanisms is operable for selectivelyinterconnecting a member of said first, second or third planetary gearset or said first or second interconnecting member with said inputshaft.
 11. The family of transmissions defined in claim 8, wherein athird of said six torque-transmitting mechanisms is selectively operablefor interconnecting a member of said first, second or third planetarygear set with said input shaft, said output shaft or a member of saidfirst, second or third planetary gear set.
 12. The family oftransmissions defined in claim 8, wherein a fourth of said sixtorque-transmitting mechanisms is selectively operable forinterconnecting a member of said first or third planetary gear set withanother member of said first, second or third planetary gear set. 13.The family of transmissions defined in claim 8, wherein a fifth of saidsix torque-transmitting mechanisms is selectively operable forinterconnecting a member of said first, second or third planetary gearset with another member of said first, second or third planetary gearset or with said stationary member.
 14. The family of transmissionsdefined in claim 8, wherein a sixth of said six torque-transmittingmechanisms is selectively operable for interconnecting a member of saidfirst, second or third planetary gear set with another member of saidfirst, second or third planetary gear set.
 15. The family oftransmissions defined in claim 8, wherein a sixth of said sixtorque-transmitting mechanisms is selectively operable forinterconnecting a member of said first or third planetary gear set withsaid stationary member.
 16. The family of transmissions defined in claim8, wherein planet carrier assembly members of each of said planetarygear sets are of the single-pinion type.
 17. The family of transmissionsin claim 8, wherein at least one planet carrier assembly member of saidplanetary gear sets is of the double-pinion type.